Gas spring fastener driving tool with improved lifter and latch mechanisms

ABSTRACT

A portable linear fastener driving tool is provided that drive staples, nails, or other linearly driven fasteners. The tool uses a gas spring principle, in which a cylinder filled with compressed gas is used to quickly force a piston through a driving stroke movement, while a driver also drives a fastener into a workpiece. The piston/driver is then moved back to its starting position by use of a rotary-to-linear lifter, and the piston again compresses the gas above the piston, thereby preparing the tool for another driving stroke. An improved lifter design has modified lifting pins that reduce the side-forces on the driver. A pivotable latch acts as a safety device, by preventing the driver from making a full driving stroke at an improper time. An improved latch design has a more durable catching surface.

CROSS-REFERENCE TO RELATED APPLICATIONS

The present application is a continuation-in-part to application Ser.No. 12/243,568, titled “FASTENER DRIVING TOOL USING A GAS SPRING,” filedon Oct. 1, 2008, which claims priority to provisional patent applicationSer. No. 60/977,678, titled “FASTENER DRIVING TOOL USING A GAS SPRING,”filed on Oct. 5, 2007.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to linear fastener driving tools, and,more particularly, directed to portable tools that drive staples, nails,or other linearly driven fasteners. The invention is specificallydisclosed as a gas spring linear fastener driving tool, in which acylinder filled with compressed gas is used to quickly force a pistonthrough a driving stroke movement, while also driving a fastener into aworkpiece. The piston is then moved back to its starting position by useof a rotary-to-linear lifter, which again compresses the gas above thepiston, thereby preparing the tool for another driving stroke. A drivermember is attached to the piston, and has protrusions along its edgesthat are used to contact the lifter member, which lifts the driverduring a return stroke. A pivotable latch is controlled to move intoeither an interfering position or a non-interfering position withrespect to the driver protrusions, and acts as a safety device, bypreventing the driver from making a full driving stroke at an impropertime. In alternative embodiments, the fastener driving tool uses adifferent type of driving device, such as a mechanical spring, to forcethe driver into a driving stroke. In other alternative embodiments, thefastener driving tool includes a rotary-to-linear lifter having multipleprotruding pins that lift the fastener driver element back to theinitiating ready position, in which at least one of the lifter pins hasa shape (or geometry) that reduces the side-loading forces between thelifter pin and the fastener driver element; and the fastener drivingtool includes a movable latch that is controlled to disengage from aslotted rib (a raised wall with spaced-apart openings) along one side ofthe driver element during a driving stroke, but also will tend to engagethe slotted rib of the driver element as a safety interlock.

2. Description of the Related Art

An early air spring fastener driving tool is disclosed in U.S. Pat. No.4,215,808, to Sollberger. The Sollberger patent used a rack andpinion-type gear to “jack” the piston back to its driving position. Aseparate motor was to be attached to a belt that was worn by the user; aseparate flexible mechanical cable was used to take the motor'smechanical output to the driving tool pinion gear, through a drivetrain.

Another air spring fastener driving tool is disclosed in U.S. Pat. No.5,720,423, to Kondo. This Kondo patent used a separate air replenishingsupply tank with an air replenishing piston to refresh the pressurizedair needed to drive a piston that in turn drove a fastener into anobject.

Another air spring fastener driving tool is disclosed in publishedpatent application no. US2006/0180631, by Pedicini, which uses a rackand pinion to move the piston back to its driving position. The rack andpinion gear are decoupled during the drive stroke, and a sensor is usedto detect this decoupling. The Pedicini tool uses a release valve toreplenish the air that is lost between nail drives.

What is needed in the art is a portable fastener driving tool that iselectrically powered, but which uses a gas spring principle of operationto drive a fastener into an object, and also uses few moving parts,which allows for simplicity of operation and provides a substantiallygas-tight system for containing the pressurized gas for the gas spring.

SUMMARY OF THE INVENTION

Accordingly, it is an advantage of the present invention to provide afastener driving tool that operates on a gas spring principle, in whichthe cylinder that contains the moving piston and driver is substantiallysurrounded by a pressure vessel (as a main storage chamber) to increasethe storage space of the pressurized gases needed for the gas springeffect.

It is another advantage of the present invention to provide a fastenerdriving tool that uses a gas spring principle to provide a quickdownward driving stroke, and uses a rotary-to-linear lifter having acam-shaped perimeter surface and multiple cylindrical protruding pinsthat lift the fastener driver element and the piston back to theinitiating firing (or driving) position.

It is a further advantage of the present invention to provide a fastenerdriving tool that operates on a gas spring principle, in which the toolhas a cylinder displacement volume and also includes a main storagechamber, and in which a volumetric ratio of the main storage chamber'svolume with respect to the cylinder's displacement volume is at least2.0:1.

It is still a further advantage of the present invention to provide afastener driving tool that operates on a gas spring principle, in whichthere is a “working storage volume” comprising a combination of a mainstorage chamber and a cylinder displacement volume, and in which thereis no gas replenishment system on-board the tool for allowing a user toreplenish the charge gases of the tool's working storage volume, therebyreducing opportunities for gas leaks.

It is yet another advantage of the present invention to provide afastener driving tool that uses a gas spring principle that uses arotary-to-linear lifter to move the driver back to its firing (ordriving) position, in which there can be a variable driving stroke byuse of multiple rotations of the lifter member.

It is still another advantage of the present invention to provide afastener driving tool that operates on a gas spring principle, in which,for a first embodiment, a movable latch is controlled by a solenoid todisengage from multiple teeth of the driver element during a drivingstroke, but also will tend to engage the teeth of the driver element asa safety interlock, and also at the maximum driver element displacementjust before a driving stroke is to occur, so that the movable latchengages the driver teeth until the user activates the tool.

It is still another advantage of the present invention to provide afastener driving tool that operates on a gas spring principle, in which,for a second embodiment, a gearbox is provided that is essentiallyself-locking from its output side, or has a one-way feature, and thusthe gearbox/lifter combination holds the driver in position just beforea driving stroke.

It is a yet further advantage of the present invention to provide afastener driving tool that operates on a gas spring principle whichincludes a system controller that allows operation in either a “bottomfiring mode” or a “trigger firing mode.”

It is a still further advantage of the present invention to provide afastener driving tool that operates on a gas spring principle in whichthe system controller has error correction capability, including thecapability of recovering from a jam of the driver element, withouthaving to completely disable the tool.

It is a further advantage of the present invention to provide a fastenerdriving tool that uses a gas spring principle to provide a quickdownward driving stroke, and uses an alternative embodimentrotary-to-linear lifter having multiple protruding pins that lift thefastener driver element and the piston back to the initiating firing (ordriving) position, in which at least one of the lifter pins has ageometry that reduces the side-loading forces between the lifter pin andthe fastener driver element.

It is still a further advantage of the present invention to provide afastener driving tool that operates on a gas spring principle, in which,for an alternative embodiment, a movable latch is controlled todisengage from a slotted rib along one side of the driver element duringa driving stroke, but also will tend to engage the slotted rib of thedriver element as a safety interlock during abnormal operatingconditions.

Additional advantages and other novel features of the invention will beset forth in part in the description that follows and in part willbecome apparent to those skilled in the art upon examination of thefollowing or may be learned with the practice of the invention.

To achieve the foregoing and other advantages, and in accordance withone aspect of the present invention, a driving mechanism for use in afastener driving tool is provided, which comprises: (a) a hollowcylinder comprising a cylindrical wall and having a movable pistontherewithin, the hollow cylinder having a first end and a second,opposite end, the hollow cylinder containing a displacement volumecreated by a stroke of the piston; (b) a guide body that issubstantially adjacent to the second end of the cylinder, the guide bodyhaving a receiving end, an exit end, and a passageway therebetween, thereceiving end being proximal to the second end of the cylinder, theguide body being configured to receive a fastener that is to be drivenfrom the exit end; (c) a driver member that is in mechanicalcommunication with the piston at a third end of the driver member, thedriver member having a fourth, opposite end that is sized and shaped topush the fastener from the exit end of the guide body, wherein thepassageway of the guide body allows the driver member to passtherethrough toward the exit end during a driving stroke and toward thereceiving end during a return stroke, the driver member, when at adriven position, protruding toward the exit end of the guide body afterthe piston moves toward the second end of the cylinder, and the drivermember, when at a ready position, being withdrawn into the guide bodyafter the piston moves toward the first end of the cylinder; (d) a mainstorage chamber that substantially surrounds at least a portion of thecylinder and is in fluidic communication with the displacement volume ofthe cylinder, wherein the main storage chamber and the displacementvolume are initially charged with a pressurized gas; and (e) a liftermember that, under first predetermined conditions, moves the drivermember from its driven position toward its ready position; wherein thecylinder and piston act as a gas spring, under second predeterminedconditions, to move the driver member from its ready position toward itsdriven position, using the pressurized gas of both the main storagechamber and the displacement volume acting on the piston, while thedriver member's fourth end contacts the fastener and moves the fastenerfrom the exit end of the guide body.

In accordance with another aspect of the present invention, a drivingmechanism for use in a fastener driving tool is provided, whichcomprises: (a) a hollow cylinder comprising a cylindrical wall andhaving a movable piston therewithin, the hollow cylinder having a firstend and a second, opposite end, the hollow cylinder containing adisplacement volume created by a stroke of the piston; (b) a mainstorage chamber that is in fluidic communication with the displacementvolume of the cylinder, wherein the main storage chamber and thedisplacement volume are initially charged with a pressurized gas; (c) aguide body that is substantially adjacent to the second end of thecylinder, the guide body having a receiving end, an exit end, and apassageway therebetween, the receiving end being proximal to the secondend of the cylinder, the guide body being configured to receive afastener that is to be driven from the exit end; (d) an elongated drivermember that is in mechanical communication with the piston at a thirdend of the driver member: (i) the driver member having a fourth,opposite end that is sized and shaped to push a fastener from the exitend of the guide body, wherein the passageway of the guide body allowsthe driver member to pass therethrough toward the exit end during adriving stroke and toward the receiving end during a return stroke, thedriver member, when at a driven position, protruding toward the exit endof the guide body after the piston moves toward the second end of thecylinder, and the driver member, when at a ready position, beingwithdrawn into the guide body after the piston moves toward the firstend of the cylinder, (ii) the driver member having at least onelongitudinal edge that is substantially parallel to a direction ofmovement of the driver member between its driven and ready positions,(iii) the driver member having at least one plurality of spaced-apartprotrusions along the at least one longitudinal edge; (e) a liftermember that exhibits a discontinuous contact surface that, atpredetermined locations along the discontinuous contact surface, makescontact with the at least one plurality of spaced-apart protrusions ofthe driver member such that, under first predetermined conditions, thelifter member is moved in a first direction and thereby causes thedriver member to be moved in a second direction from its driven positiontoward its ready position; and (f) a latch member that has a catchingsurface and a sliding surface, wherein: (i) under third predeterminedconditions, the latch member is controlled by a separate device and isforced into a non-catching position such that its catching surface doesnot interfere with the at least one plurality of spaced-apartprotrusions of the driver member, thereby allowing the driver member tomove in a third direction from its ready position to its drivenposition; and (ii) under fourth predetermined conditions, during whichthe driver member is being moved in the second direction from its drivenposition to its ready position, the separate device releases the latchmember so that the latch member is not forced into a non-catchingposition, the latch member is directed toward a catching position,however, the sliding surface of the latch member allows the at least oneplurality of spaced-apart protrusions of the driver member to slidealong the latch member without being stopped so long as the drivermember remains moving in the second direction; wherein the cylinder andpiston act as a gas spring, under second predetermined conditions, tomove the driver member from its ready position toward its drivenposition, using the pressurized gas of both the main storage chamber andthe displacement volume acting on the piston, while the driver member'sfourth end contacts the fastener and moves the fastener from the exitend of the guide body.

In accordance with yet another aspect of the present invention, adriving mechanism for use in a fastener driving tool is provided, whichcomprises: (a) a hollow cylinder comprising a cylindrical wall andhaving a movable piston therewithin, the hollow cylinder having a firstend and a second, opposite end, the hollow cylinder containing adisplacement volume created by a stroke of the piston; (b) a mainstorage chamber that is in fluidic communication with the displacementvolume of the cylinder, wherein the main storage chamber and thedisplacement volume are initially charged with a pressurized gas; (c) aguide body that is substantially adjacent to the second end of thecylinder, the guide body having a receiving end, an exit end, and apassageway therebetween, the receiving end being proximal to the secondend of the cylinder, the guide body having an opening for receiving afastener that is to be driven from the exit end; (d) an elongated drivermember that is in mechanical communication with the piston at a thirdend of the driver member: (i) the driver member having a fourth,opposite end that is sized and shaped to push a fastener into anexternal workpiece, wherein the passageway of the guide body allows thedriver member to pass therethrough toward the exit end during a drivingstroke and toward the receiving end during a return stroke, the drivermember, when at a driven position, protruding toward the exit end of theguide body after the piston moves toward the second end of the cylinder,and the driver member, when at a ready position, being withdrawn intothe guide body after the piston moves toward the first end of thecylinder; (ii) the driver member having a first longitudinal edge, (iii)the driver member having a first plurality of spaced-apart protrusionsalong the first longitudinal edge; and (e) a lifter member that exhibitsan outer shape, in which its outer shape defines a perimeter of asurface: (i) the lifter member being rotated, under first predeterminedconditions, by a drive member that is in mechanical communication withthe lifter member, (ii) the lifter member having a plurality ofextensions that protrude from the surface, and under the firstpredetermined conditions, the plurality of extensions are brought intomechanical contact with the first plurality of spaced-apart protrusionsalong the first longitudinal edge of the driver member during the returnstroke, and thereby moves the driver member from its driven positiontoward its ready position, and (iii) the lifter member beingpositionable, under second predetermined conditions such that a portionof the perimeter of the lifter member and the plurality of extensions isnot proximal to the first plurality of spaced-apart protrusions of thedriver member, and thereby prevents the plurality of extensions of thelifter member from mechanically interfering with the first plurality ofspaced-apart protrusions of the driver member during the driving strokein which the driver member is moved from its ready position toward itsdriven position.

In accordance with still another aspect of the present invention, adriving mechanism for use in a fastener driving tool is provided, whichcomprises: (a) a guide body that has a receiving end, an exit end, and apassageway therebetween, the guide body being configured to receive afastener that is to be driven from the exit end; (b) a driver actuationdevice that has a first end and a second end, the second end beingmovable; (c) an elongated driver member that is in mechanicalcommunication with the second end of the driver actuation device at athird end of the driver member: (i) the driver member having a fourth,opposite end that is sized and shaped to push a fastener from the exitend of the guide body, wherein the passageway of the guide body allowsthe driver member to pass therethrough toward the exit end during adriving stroke and toward the receiving end during a return stroke, thedriver member, when at a driven position, protruding toward the exit endof the guide body, and the driver member, when at a ready position,being withdrawn into the guide body, (ii) the driver member having atleast one longitudinal edge and having a direction of movement betweenits driven and ready positions, (iii) the driver member having at leastone plurality of spaced-apart protrusions along the at least onelongitudinal edge; and (d) a lifter member that exhibits a discontinuouscontact surface that, at predetermined locations along the discontinuouscontact surface, makes contact with the at least one plurality ofspaced-apart protrusions of the driver member such that the liftermember is moved in a first direction and thereby causes the drivermember to be moved from its driven position toward its ready position;wherein: (e) the lifter member, under first predetermined conditions,forces the driver member to undergo a return stroke and move toward theready position; and (f) the driver actuation device, under secondpredetermined conditions, forces the driver member to undergo a drivingstroke and move toward the driven position.

In accordance with a further aspect of the present invention, a drivingmechanism for use in a fastener driving tool is provided, whichcomprises: (a) a hollow cylinder comprising a cylindrical wall andhaving a movable piston therewithin, the hollow cylinder having a firstend and a second, opposite end, the hollow cylinder containing adisplacement volume created by a stroke of the piston; (b) a guide bodythat is substantially adjacent to the second end of the cylinder, theguide body having a receiving end, an exit end, and a passagewaytherebetween, the receiving end being proximal to the second end of thecylinder, the guide body being configured to receive a fastener that isto be driven from the exit end; (c) an elongated driver member that isin mechanical communication with the piston at a third end of the drivermember: (i) the driver member having a fourth, opposite end that issized and shaped to push a fastener into an external workpiece, whereinthe passageway of the guide body allows the driver member to passtherethrough toward the exit end during a driving stroke and toward thereceiving end during a return stroke, the driver member, when at adriven position, protruding toward the exit end of the guide body afterthe piston moves toward the second end of the cylinder, and the drivermember, when at a ready position, being withdrawn into the guide bodyafter the piston moves toward the first end of the cylinder; (ii) thedriver member having a first longitudinal edge and having a direction ofmovement between its driven and ready positions, (iii) the driver memberhaving a first plurality of spaced-apart protrusions along the firstlongitudinal edge; (d) a lifter member that, under first predeterminedconditions, moves the driver member from its driven position toward itsready position, wherein: (i) the lifter member is rotated, under firstpredetermined conditions, by a drive shaft that is in mechanicalcommunication with the lifter member; (ii) the lifter member has aplurality of extensions that protrude from a surface of the liftermember, and under the first predetermined conditions, the plurality ofextensions are brought into mechanical contact with at least one of thefirst plurality of spaced-apart protrusions along the first longitudinaledge of the driver member, and thereby, under the first predeterminedconditions, moves the driver member from its driven position toward itsready position, and (iii) the lifter member is positionable, undersecond predetermined conditions such that the plurality of extensions ofthe lifter member are prevented from mechanically interfering with thefirst plurality of spaced-apart protrusions along the first longitudinaledge of the driver member during the driving stroke in which the drivermember is moved from its ready position toward its driven position; and(e) a driver actuation device that, under second predeterminedconditions, forces the driver member to undergo a driving stroke andmove toward the driven position.

In accordance with a yet further aspect of the present invention, adriving mechanism for use in a fastener driving tool is provided, whichcomprises: (a) a guide body that has a receiving end, an exit end, and apassageway therebetween, the guide body being configured to receive afastener that is to be driven from the exit end; (b) a driver actuationdevice that has a first end and a second end, the second end beingmovable; (c) an elongated driver member that is in mechanicalcommunication with the second end of the driver actuation device at athird end of the driver member: (i) the driver member having a fourth,opposite end that is sized and shaped to push a fastener from the exitend of the guide body, wherein the passageway of the guide body allowsthe driver member to pass therethrough toward the exit end during adriving stroke and toward the receiving end during a return stroke, thedriver member, when at a driven position, protruding toward the exit endof the guide body, and the driver member, when at a ready position,being withdrawn into the guide body, (ii) the driver member having atleast one longitudinal edge and having a direction of movement betweenits driven and ready positions, (iii) the driver member having at leastone plurality of spaced-apart protrusions along the at least onelongitudinal edge; and (d) a lifter member that exhibits a discontinuouscontact surface that, at predetermined locations along the discontinuouscontact surface, makes contact with the at least one plurality ofspaced-apart protrusions of the driver member such that the liftermember is moved in a first direction and thereby causes the drivermember to be moved in a second direction from its driven position towardits ready position during the return stroke; and (e) a movable latchmember that: (i) does not prevent a movement of the driver member whenthe driver member moves in the second direction; (ii) under normalcircumstance, does not prevent a movement of the driver member when thedriver member moves in a third direction from its ready position to itsdriven position during the driving stroke; and (iii) under abnormalcircumstances, prevents a movement of the driver member when the drivermember moves in the third direction; wherein: (f) the lifter member,under first predetermined conditions, forces the driver member toundergo a return stroke and move toward the ready position; and (g) thedriver actuation device, under second predetermined conditions, forcesthe driver member to undergo a driving stroke and move toward the drivenposition.

In accordance with a another aspect of the present invention, a drivingmechanism for use in a fastener driving tool is provided, whichcomprises: (a) a guide body that has a receiving end, an exit end, and apassageway therebetween, the guide body being configured to receive afastener that is to be driven from the exit end; (b) a movable driveractuation device; (c) an elongated driver member that is in mechanicalcommunication with the movable driver actuation device at a first end ofthe driver member, the driver member having a second, opposite end thatis sized and shaped to push a fastener from the exit end of the guidebody, the driver member having a direction of movement between a drivenposition and a ready position, the driver member having a longitudinaledge, the driver member having a plurality of spaced-apart protrusionsalong the longitudinal edge; and (d) a lifter member that exhibits acontoured contact surface that, at predetermined locations along thecontoured contact surface, makes contact with the plurality ofspaced-apart protrusions of the driver member such that, as the liftermember is moved in a first direction, the lifter member causes thedriver member to be moved from its driven position toward its readyposition, the contoured contact surface comprising a plurality ofspaced-apart extensions, a final one of the spaced-apart plurality ofextensions having a shape comprising: an arcuate shape for a portion ofits outer perimeter, and at least two outer corners with a substantiallylinear face therebetween; wherein the shape for the final one of theplurality of extensions reduces side-loading forces between the liftermember and the elongated driver member.

In accordance with a yet another aspect of the present invention, adriving mechanism for use in a fastener driving tool is provided, whichcomprises: (a) a guide body that has a receiving end, an exit end, and apassageway therebetween, the guide body being configured to receive afastener that is to be driven from the exit end; (b) a movable driveractuation device; (c) an elongated driver member that is in mechanicalcommunication with the movable driver actuation device at a first end ofthe driver member, the driver member having a second, opposite end thatis sized and shaped to push a fastener from the exit end of the guidebody, the driver member having a direction of movement between a drivenposition and a ready position, the driver member having a longitudinaledge, the driver member having a plurality of spaced-apart protrusionsalong the longitudinal edge; and (d) a lifter member that exhibits acontoured contact surface that, at predetermined locations along thecontoured contact surface, makes contact with the plurality ofspaced-apart protrusions of the driver member such that, as the liftermember is moved in a first direction, the lifter member causes thedriver member to be moved from its driven position toward its readyposition, the contoured contact surface comprising a plurality ofspaced-apart extensions, at least one of the spaced-apart plurality ofextensions having an arcuate surface for a first portion of its outerperimeter, and a cut-off face for a second portion of its outerperimeter, wherein a first outer corner provides an abrupt angularchange in direction along the outer perimeter at a location between thefirst and second portions of the outer perimeter.

In accordance with a still another aspect of the present invention, adriving mechanism for use in a fastener driving tool is provided, whichcomprises: (a) a guide body that has a receiving end, an exit end, and apassageway therebetween, the guide body being configured to receive afastener that is to be driven from the exit end; (b) a movable driveractuation device; (c) an elongated driver member that is in mechanicalcommunication with the movable driver actuation device at a first end ofthe driver member, the driver member having a second, opposite end thatis sized and shaped to push a fastener from the exit end of the guidebody, the driver member having a direction of movement between a drivenposition and a ready position, the driver member having a plurality ofspaced-apart protrusions along a first longitudinal edge, the drivermember having a plurality of spaced-apart openings formed in a raisedwall along a second longitudinal edge that is substantially parallel tothe first longitudinal edge; (d) a lifter member that exhibits acontoured contact surface that, at predetermined locations along thecontoured contact surface, makes contact with the plurality ofspaced-apart protrusions of the driver member such that, as the liftermember is moved in a first direction, the lifter member causes thedriver member to be moved in a second direction, from its drivenposition toward its ready position; and (e) a movable latch member thatis positioned proximal to the second longitudinal edge of the drivermember, the raised wall presenting a substantially planar surface forthe latch member to work against, such that the latch member may slidealong the raised wall except where one of the spaced-apart openingappears in the raised wall, at which location the latch member is biasedto move into the spaced-apart opening; wherein, during operation, thelatch member: (i) does not prevent a movement of the driver member whenthe driver member moves in the second direction; (ii) under normalcircumstances, does not prevent a movement of the driver member when thedriver member moves in a third direction that is substantially oppositefrom the second direction, during a driving stroke; and (iii) underabnormal circumstances, as a safety feature, the latch member prevents asubstantial movement of the driver member when the driver member movesin the third direction in the event that normal operation between thelifter member and the driver member fails.

Still other advantages of the present invention will become apparent tothose skilled in this art from the following description and drawingswherein there is described and shown a preferred embodiment of thisinvention in one of the best modes contemplated for carrying out theinvention. As will be realized, the invention is capable of otherdifferent embodiments, and its several details are capable ofmodification in various, obvious aspects all without departing from theinvention. Accordingly, the drawings and descriptions will be regardedas illustrative in nature and not as restrictive.

BRIEF DESCRIPTION OF THE DRAWINGS

The above-mentioned and other features and advantages of this invention,and the manner of attaining them, will become more apparent and theinvention will be better understood by reference to the followingdescription of an embodiment of the invention taken in conjunction withthe accompanying drawings, wherein:

FIG. 1 is a side view in partial cross-section of a first embodiment ofa fastener driving tool constructed according to the principles of thepresent invention.

FIG. 2 is a perspective view mainly from the side, but also from above,and in partial cross-section, of the gas spring cylinder mechanism ofthe first embodiment fastener driving tool of FIG. 1.

FIG. 3 is another perspective view from the side and somewhat from aboveand in partial cross-section of the gas spring cylinder portion of thefirst embodiment fastener driving tool of FIG. 1, better showing thedriver mechanism, with the piston at its lowest “driven” position.

FIG. 4 is another perspective view from the side and somewhat from aboveand in partial cross-section of the gas spring cylinder portion of thefirst embodiment fastener driving tool of FIG. 1, in which the driverand piston are near their top-most position, but still latched and notquite ready for firing (driving).

FIG. 5 is another perspective view from the side and somewhat from aboveand in partial cross-section of the gas spring cylinder portion of thefirst embodiment fastener driving tool of FIG. 1, in which the driverand piston are near their top-most position, in which the mechanism isnow unlatched and ready for firing (driving).

FIG. 6 is a perspective view of driver, rotary-to-linear lifter, andlatch portions of the driver mechanism for the first embodiment fastenerdriving tool of FIG. 1.

FIG. 7 is another perspective view from a different angle of the samecomponents of FIG. 6.

FIG. 8 is a side view in partial cross-section of major portions of thedriving mechanisms for the first embodiment fastener driving tool ofFIG. 1.

FIG. 9 is a perspective view mainly from the left side, but angled tobetter see the details of the latch mechanism including its solenoid,for the first embodiment fastener driving tool of FIG. 1.

FIG. 10 is an elevational side view in cross-section of some of thedetails of the cylinder/piston components for the first embodimentfastener driving tool of FIG. 1.

FIG. 11 is an elevational side view in cross-section of some of thedetails of the cylinder/piston components for an alternative embodimentthat could be used with the first embodiment fastener driving tool ofFIG. 1.

FIG. 12 is a perspective view from the opposite side of therotary-to-linear lifter, used in the first embodiment fastener drivingtool of FIG. 1.

FIG. 13 (FIGS. 13A-13B) is a first portion of a flow chart showing someof the important logical steps performed by the controller of the firstembodiment fastener driving tool of FIG. 1.

FIG. 14 (FIGS. 14A-14C) is a second portion of the flow chart of FIG.13.

FIG. 15 is a third portion of the flow chart of FIG. 13.

FIG. 16 is a side, elevational view of a second embodiment of a fastenerdriving tool constructed according to the principles of the presentinvention.

FIG. 17 is a side view in partial cross-section of the second embodimentfastener driving tool of FIG. 16.

FIG. 18 is a front, elevational view in partial cross-section of thesecond embodiment fastener driving tool of FIG. 16.

FIG. 19 is a perspective view mainly from the side, but also from above,and in partial cross-section, of the gas spring cylinder mechanism ofthe second embodiment fastener driving tool of FIG. 16.

FIG. 20 is another perspective view from the side and somewhat fromabove and in partial cross-section of the gas spring cylinder portion ofthe second embodiment fastener driving tool of FIG. 16, better showingthe driver mechanism, with the piston at its lowest “driven” position.

FIG. 21 is another perspective view from the side and somewhat fromabove and in partial cross-section of the gas spring cylinder portion ofthe second embodiment fastener driving tool of FIG. 16, in which thedriver and piston are near their top-most position, and the latch is inits interfering position.

FIG. 22 is another perspective view from the side and somewhat fromabove and in partial cross-section of the gas spring cylinder portion ofthe second embodiment fastener driving tool of FIG. 16, in which thedriver and piston are near their top-most position, and the latch is inits non-interfering position, in which the mechanism is now ready forfiring (driving).

FIG. 23 is a perspective view of driver, rotary-to-linear lifter, andlatch portions of the driver mechanism for the second embodimentfastener driving tool of FIG. 16.

FIG. 24 is another perspective view from a different angle of the samecomponents of FIG. 23.

FIG. 25 is a side elevational view in partial cross-section of majorportions of the driving mechanisms for the second embodiment fastenerdriving tool of FIG. 16.

FIG. 26 is a side view in partial cross-section of major portions of thedriving mechanisms for a third embodiment fastener driving tool somewhatsimilar to that of FIG. 16, however, using a mechanical drive springattached to the driver, rather than a gas drive spring in a cylinder.

FIG. 27 is a perspective view mainly from the left side, but angled tobetter see the details of the latch mechanism including its solenoid,for the second embodiment fastener driving tool of FIG. 16.

FIG. 28 is an elevational side view in cross-section of some of thedetails of the cylinder/piston components for the second embodimentfastener driving tool of FIG. 16.

FIG. 29 is a perspective view from the opposite side of therotary-to-linear lifter, used in the second embodiment fastener drivingtool of FIG. 16.

FIG. 30 are perspective views showing some of the details of a firstparticular arrangement of a rotary-to-linear lifter and the surfacesthat engage the driver, in which the lifter exhibits a single “tooth”and has an arcuate outer perimeter shape, which can be used with thefastener driving tools of FIG. 1 or FIG. 16.

FIG. 31 are perspective views showing some of the details of a secondparticular arrangement of a rotary-to-linear lifter and the surfacesthat engage the driver, in which the lifter exhibits two “teeth” and hasan irregular outer perimeter shape, which can be used with the fastenerdriving tools of FIG. 1 or FIG. 16.

FIG. 32 are perspective views showing some of the details of a thirdparticular arrangement of a rotary-to-linear lifter and the surfacesthat engage the driver, in which the lifter exhibits three “teeth” andhas a circular outer perimeter shape, which can be used with thefastener driving tools of FIG. 1 or FIG. 16.

FIG. 33 are perspective views showing some of the details of a thirdparticular arrangement of a rotary-to-linear lifter and the surfacesthat engage the driver, in which the lifter exhibits three “teeth” andhas a square outer perimeter shape, which can be used with the fastenerdriving tools of FIG. 1 or FIG. 16.

FIG. 34 is a side, elevational view of a third embodiment of a fastenerdriving tool constructed according to the principles of the presentinvention, in which the storage chamber does not surround the workingcylinder.

FIG. 35 (FIGS. 35A-35C) is a first portion of a flow chart showing someof the important logical steps performed by the controller of the secondembodiment fastener driving tool of FIG. 16.

FIG. 36 (FIGS. 36A-36D) is a second portion of the flow chart of FIG.35.

FIG. 37 is a third portion of the flow chart of FIG. 35.

FIG. 38 is a diagrammatic view of an alternative embodiment liftermechanism, showing the face of the lifter's surface at a normal angle,so as to show the shapes of the lifter pins and their orientations onthe lifter's surface.

FIG. 39 is a side view in partial cross-section of certain portions ofthe driving mechanisms showing another alternative embodiment for thefastener driving tool of FIG. 1, which uses the alternative embodimentlifter mechanism of FIG. 38, in which the “first pin” of the lifter ismaking contact with one of the teeth of the driver element.

FIG. 40 is a side view in partial cross-section of certain portions ofthe driving mechanisms showing the alternative embodiment liftermechanism of FIG. 39, in which the “second pin” of the lifter is makingcontact with one of the teeth of the driver element.

FIG. 41 is a side view in partial cross-section of certain portions ofthe driving mechanisms showing the alternative embodiment liftermechanism of FIG. 39, in which the “third pin” of the lifter is makingcontact with one of the teeth of the driver element, and is about torelease from that contact with the driver tooth, to allow a drivingstroke.

FIG. 42 is a perspective view from the side and somewhat from above ofthe driver, rotary-to-linear lifter, and latch portions of the drivermechanism for the alternative embodiment fastener driving tool of FIG.39, showing further details of an improved alternative embodiment driverelement and an improved latch mechanism.

FIG. 43 is a pin contact lift force diagram of an entirely round “third”lifter pin, such as that seen in FIG. 12, for the first embodimentfastener driving tool of FIG. 1.

FIG. 44 is a pin contact lift force diagram of an improved design“third” lifter pin, such as that seen in FIG. 38, for the alternativeembodiment lifter mechanism of FIG. 39.

FIG. 45 is a diagrammatic view of another alternative embodiment liftermechanism, showing the face of the lifter's surface at a normal angle,so as to show the shapes of the lifter pins and their orientations onthe lifter's surface.

Corresponding reference characters indicate corresponding partsthroughout the several views. The exemplification set out hereinillustrates one preferred embodiment of the invention, in one form, andsuch exemplification is not to be construed as limiting the scope of theinvention in any manner.

DETAILED DESCRIPTION OF THE INVENTION

The terms “first” and “second” preceding an element name, e.g., firstpin, second pin, etc., are used for identification purposes todistinguish between similar elements, and are not intended tonecessarily imply order, nor are the terms “first” and “second” intendedto preclude the inclusion of additional similar elements.

Reference will now be made in detail to the present preferred embodimentof the invention, an example of which is illustrated in the accompanyingdrawings, wherein like numerals indicate the same elements throughoutthe views.

Referring now to FIG. 1, a first embodiment of a fastener driving toolis generally designated by the reference numeral 10. This tool 10 ismainly designed to linearly drive fasteners such as nails and staples.Tool 10 includes a handle portion 12, a fastener driver portion 14, afastener magazine portion 16, and a fastener exit portion 18.

A “left” outer cover of the driver portion is indicated at 20. A “top”cover is indicated at 22, while a “front” outer cover or “housing” ofthe driver portion is indicated at 24. A “rear” cover for the handleportion is indicated at 26 (which is also the battery pack cover), whilea “rear” cover of the magazine portion is indicated at 28. It will beunderstood that the various directional nomenclature provided above iswith respect to the illustration of FIG. 1, and the first embodimentfastener driving tool 10 can be used in many other angular positions,without departing from the principles of the present invention.

The area of the first embodiment tool 10 in which a fastener is releasedis indicated approximately by the reference numeral 30, which is the“bottom” of the fastener exit portion of tool 10. Before the tool isactuated, a safety contact element 32 extends beyond the bottom 30 ofthe fastener exit, and this extension of the safety contact element isdepicted at 34, which is the bottom or “front” portion of the safetycontact element. Other elements that are depicted in FIG. 1 include aguide body 36 and a front cover 38, which are in mechanicalcommunication with the magazine portion 16.

Reference numeral 60 indicates a magazine housing, while referencenumeral 62 indicates a fastener track through which the individualfasteners run therethrough while they remain within the magazine portion16. A feeder carriage 64 is used to feed an individual fastener from themagazine into the drive mechanism area, and a back plate 66 is used tocarry an individual fastener while it is being driven. In theillustrated embodiment, the feeder carriage 64 positions a fastener to aposition within the guide body that is coincident with the path of thedriver member 90, so that when the driver 90 moves through a drivingstroke, its driving end will basically intercept the fastener and carrythat fastener to the exit end of the tool 10, essentially at the bottomportion 30 of the tool's exit area.

The first embodiment fastener driving tool 10 also includes a motor 40which acts as a prime mover for the tool, and which has an output thatdrives a gearbox 42. An output shaft 44 of the gearbox drives a lifterdrive shaft 102 (see FIG. 2). A solenoid 46 is depicted on FIG. 1, andfurther details of its operation are discussed below. A battery 48 isattached near the rear of the handle portion 12, and this batteryprovides electrical power for the motor 40 as well as for a controlsystem.

A printed circuit board that contains a controller is generallydesignated by the reference numeral 50, and is placed within the handleportion 12 in this embodiment. A trigger switch 52 is activated by atrigger actuator 54. As can been seen by viewing FIG. 1, the handleportion 12 is designed for gripping by a human hand, and the triggeractuator 54 is designed for linear actuation by a person's finger whilegripping the handle portion 12. Trigger switch 52 provides an input tothe control system 50. There are also other input devices for thecontroller, however those input devices are not seen in FIG. 1.

The controller will typically include a microprocessor or amicrocomputer device that acts as a processing circuit. At least onememory circuit will also typically be part of the controller, includingRandom Access Memory (RAM) and Read Only Memory (ROM) devices. To storeuser-inputted information (if applicable for a particular tool model), anon-volatile memory device would typically be included, such as EEPROM,NVRAM, or a Flash memory device.

Referring now to FIG. 2, a working cylinder subassembly is designated bythe reference numeral 71, and this is included as part of the fastenerdriver portion 14. On FIG. 2, the working cylinder 71 includes acylinder wall 70, and within this cylinder wall 70 is a piston 80, amovable piston stop 82, and a stationary piston stop 84 (see FIG. 3).Part of the piston mechanism of this embodiment includes a piston seal86, a piston guide ring 88, and a piston scraper 89 (see FIG. 10).Surrounding, in the illustrated embodiment, the cylinder wall 70 is amain storage chamber 74 (also sometimes referred to herein as a“pressure vessel storage space”) and an outer pressure vessel wall 78(which corresponds to the “front” cover 24 of FIG. 1, along the leftportion of this view). At the top (as seen on FIG. 2) of the fastenerdriver portion 14 is a top cap 72 for the cylinder mechanism.

Also within the fastener driver portion 14 are mechanisms that willactually drive a fastener into a solid object. This includes a driver90, a cylinder “venting chamber” 94 (which would typically always be atatmospheric pressure), a driver track 98 (see FIG. 4), arotary-to-linear lifter 100, and a latch 120. The driver 90 is alsosometimes referred to herein as a “driver member” and therotary-to-lifter 100 is also sometimes referred to herein as a “liftermember,” or simply as a “lifter.” Driver 90 is rather elongated, and asan individual element can best be seen in FIGS. 6 and 7. There aremultiple “teeth” 92 that are positioned along the driver. In theillustrated embodiment, these teeth 92 are spaced-apart not only in atransverse direction from the elongated centerline of driver 90, butthey are also spaced-apart from one another along the outer longitudinaledges of the driver 90. The positions of teeth 92 are clearlyillustrated in FIGS. 6 and 7. It will be understood that the precisepositions for the teeth 92 could be different from those illustrated forthe driver 90 without departing from the principles of the presentinvention.

There is a cylinder base 96 that mainly separates the gas pressureportions of the fastener driver portion 14 from the mechanical portionsof that driver portion 14. The venting of air from the cylinder ventingchamber 94 passes through the cylinder base 96, as seen at a vent 150(see FIG. 3). The mechanical portions of FIG. 2 begin with arotary-to-linear lifter 100 which was briefly mentioned above, alongwith a lifter drive shaft 102. Drive shaft 102 protrudes through thecenter portions of the fastener driver portion 14 and through the centerof the lifter 100, and this shaft is used to rotate the lifter, asdesired by the control system.

Lifter 100 is not designed with an entirely circular outer perimeter,but instead is arcuate and portions of its perimeter exhibit aneccentric shape of a cam (see FIG. 12). A portion of the lifter's outerperimeter is mainly circular for about half of a circle (designated bythe reference numeral 116), but the other half of the lifter's outerperimeter is more eccentric, which provides an elliptical surface thatis designated by the reference numeral 110. The rotary-to-linear lifter100 also includes three cylindrical protrusions (or “extensions”) thatwill also be referred to herein as “pins.” The first such pin (“pin 1”)is designated 104, the second pin (“pin 2”) is designated 106, while thethird pin (“pin 3”) is designated 108. These pins are all viewed on FIG.12. Furthermore, there is a fourth cylindrical pin (“pin 4”) thatprotrudes from the opposite side of the lifter 100, which fourth pin isdesignated 114, and which can be viewed on several of the other figures,namely FIGS. 2-8.

It should be noted that FIGS. 2-8 also depict a “back” side of the firstthree pins 104, 106, and 108, in which these views essentially show a“boss portion” of those pins. These boss portions of the pins 104, 106,108 are not entirely necessary for the proper functioning of therotary-to-linear lifter 100, however, the boss portions are illustratedin the figures of this patent document for ease of description. (Inother words, the surface of the lifter 100 could be perfectly smooth atthose locations rather than exhibiting a “boss.”) It should beunderstood that the “working side” of these three pins 104, 106, and 108is on the opposite side of the lifter 100 in the views of FIGS. 2-8, andthis working side is directly illustrated in FIG. 12. When discussingthese pins 104, 106, and 108 with respect to FIGS. 2-8 in this writtendescription, it is with reference to the “boss side” of those pins;however, the effects of the “working side” of those pins is discussed insome detail with respect to other structures that are also illustratedon FIGS. 2-8. It should also be noted that pins 104, 106, 108, and 114are illustrated as having circular cross-sectional shapes, which isdesirable for this embodiment, although other cross-sectional shapescould instead be used without departing from the principles of thepresent invention, particularly for the fourth pin 114.

The latch 120 that was briefly noted above is depicted on FIG. 2, andhas a latch shaft 122 protruding therethrough, and this shaft rotatesthe latch 120 as determined by the controller. Latch 120 includes alatch “catching surface” at 124, and this will be more fully explainedbelow. In FIG. 2, there is an internal cover 112 that is a portion ofthe back plate 66, and hides some of the other mechanical componentsthat will be visible in other views.

In FIG. 2, the piston 80 is not quite at its uppermost or top-mostposition, and a gas pressure chamber 76 can be seen above the top-mostarea of the piston, near the piston seal 86. It will be understood thatthe gas pressure chamber 76 and the main storage chamber (or storagespace) 74 are in fluidic communication with one another. It will also beunderstood that the portion to the interior of the cylinder wall 70forms a displacement volume that is created by the stroke of the piston80. In other words, the gas pressure chamber 76 is not a fixed volume,but this chamber will vary in volume as the piston 80 moves up and down(as seen in FIG. 2). This type of mechanical arrangement is oftenreferred to as a “displacement volume,” and that terminology will mainlybe used herein for this non-fixed volume 76.

It will be further understood that the main storage chamber 74preferably comprises a fixed volume, which typically would make it lessexpensive to manufacture; however, it is not an absolute requirementthat the main storage chamber actually be of a fixed volume. It would bepossible to allow a portion of this chamber 74 to deform in size and/orshape so that the size of its volume would actually change, duringoperation of the present invention, without departing from theprinciples of the present invention.

In the illustrated embodiment for the first embodiment fastener drivingtool 10, the main storage chamber 74 substantially surrounds the workingcylinder 71. Moreover, the main storage chamber 74 is annular in shape,and it is basically co-axial with the cylinder 71. This is a preferredconfiguration of the illustrated first embodiment, but it will beunderstood that alternative physical arrangements could be designedwithout departing from the principles of the present invention.

Referring now to FIG. 3, the piston is depicted at its bottom-mosttravel position, and in this configuration, the displacement volume 76and the main storage chamber 74 are at their largest combined volumes,while the cylinder venting chamber 94 is at its minimum volume. Thisbottom position is also sometimes referred to herein as the “drivenposition.”

In FIG. 3, the movable piston stop 82 is now in contact with thestationary piston stop 84, which is why the cylinder venting chamber 94is at its minimum (or zero) volume. In FIG. 3, the driver 90 is also atits bottom-most travel position, and its lower-most tip can be seenextending out the exit port at the bottom of the guide body 36.

In FIG. 3, the rotary-to-linear lifter 100 and the latch 120 are intheir respective positions at the end of a firing (driving) stroke, andthe latch 120 has its latching surface 124 in a location that will notinterfere with the teeth 92 of the driver 90. This is necessary so thatthe driver 90 can make a linear stroke from its top-most position to itsbottom-most position. However, the latch 120 will later be slightlyrotated by the latch shaft 122 (which is spring-loaded) so that itscatching surface 124 will be able to interfere with the teeth 92.

In the configuration depicted on FIG. 3, the fastener driving tool 10has been used to drive a fastener, and the tool now must cause thedriver 90 to be “lifted” back to its top-most position for a new firing(driving) stroke. This is accomplished by rotating the lifter 100, whichis actuated by the motor 40, through its gearbox 42, etc.

As rotary-to-linear lifter 100 rotates counterclockwise (as seen in FIG.3) at least one of its pins 104, 106, or 108 will come into contact withone of the teeth 92 along the left side (as seen in FIG. 3) of thedriver 90. This will cause the driver 90 to be “lifted” upward (as seenin FIG. 3). As the lifter 100 rotates, one of the teeth 92 will be incontact with one of the rotating pins 104, 106, 108 throughout a portionof the rotational travel of the lifter, and the “next” pin will thencome into contact with the “next” tooth 92 so that the driver 90continues to be moved upward. This will remain true until the eccentriccam surface 110 comes into play, and since there are no “working” lifterpins protruding along that surface, the driver 90 will not continue tobe driven upward while the eccentric cam surface 110 is positioned alongthe right portion (as seen in FIG. 3) of the rotary-to-linear lifter100. However, when this occurs, the latch 120, which is spring-loaded,will have its latch catching surface 124 in a proper location to “catch”the closest tooth 92 along the right-hand side (as seen in FIG. 3) ofthe driver 90, thereby preventing the driver from falling downward forany significant distance. After this occurs, the “next” lifter pin(which will be the pin 104) will then come along and again make contactwith one of the teeth 92 along the left-hand side (as seen in FIG. 3) ofthe driver 90, thereby continuing to lift the driver toward the top (asseen in FIG. 3) of the cylinder 71.

In the illustrated embodiment of the first embodiment fastener drivingtool 10, the rotary-to-linear lifter 100 makes two complete rotations tolift the driver 90 from its bottom-most position to its top-mostposition. (The upper position is also sometimes referred to herein asthe “ready position.”) At the end of the second rotation, the parts willbe configured as illustrated in FIG. 4. The piston 80 is once again nearthe top of the cylinder 71, and the combined volumes of the main storagechamber 74 and displacement volume 76 have now been reduced to a smallervolume, which means their gases are under a greater pressure, since thegas that was above the piston and in chamber 74 was compressed duringthe lift of the driver. (As noted above, the actual volume of the mainstorage chamber 74 does not change in the illustrated embodiment.)During the lift of the driver, the latch 120 was “engaged” with theteeth 92, however, the latch has a smooth surface in one direction thatallows the teeth 92 to push the latch out of the way during the upwardlift of the driver. This is much like a ratchet-type action, rememberingthat the latch is spring-loaded so as to act in this manner.

In FIG. 4, the “last” tooth 126 along the right-hand side (as seen inFIG. 4) of the driver 90 is engaged with the latch catching surface 124,and so latch 120 now prevents the driver from being moved downward (asseen in this view). The third pin 108 is still in contact with thelower-most tooth 92 along the left-hand side (as seen in FIG. 4) of thedriver 90, at this point in the rotational travel of therotary-to-linear lifter 100. There is a sensor which, in the illustratedembodiment, is a limit switch 130 (see FIG. 8), that detects therotational movements of the lifter 100. This sensor detects the fourthpin 114, as discussed below in greater detail.

When the sensor 130 detects the fourth pin 114 a first time (in thisembodiment), the control system turns off the solenoid 46, which willthen allow the latch 120 to engage the right-hand teeth (in these views)of the lifter 100. Note that the solenoid can also be turned off earlierduring the lift, if desired. When sensor 130 detects this pin 114 asecond time (in this embodiment), the current to the motor 40 is turnedoff, and the motor thus is de-energized and stops the lifting action ofthe driver 90. As described herein, the solenoid 46 acts as a latchactuator.

Due to the gas pressure above the piston 80, the driver/pistonsubassembly will drift downward (in these views) a small distance untilthe tooth 126 contacts the latch surface 124. This is the positionillustrated in FIG. 4 of these components, and this configuration isconsidered to be the “rest” position of the tool. Although the gaspressure in the combined main storage chamber 74 and displacement volume76 is at its maximum, the latch 120 prevents the driver from being movedfurther downward, so the piston is essentially locked in this positionuntil something else occurs. In a preferred mode of the invention, thepressure vessel may be pressurized at about 100 PSIG to 120 PSIG.

When it is time to drive a fastener, the next action in the illustratedfirst embodiment is to cause the motor 40 to become energized onceagain. This occurs by two independent actions by the user: in some modesof the invention, these two independent actions can occur in eitherorder. (There is also an optional “restrictive mode” of operation, inwhich the two independent actions must occur in a specific order.) Thesetwo actions are: pressing the nose 34 of the safety contact element 32against a solid surface, and depressing the trigger actuator 54. Thetrigger actuator will cause the trigger switch 52 to change state, whichis one condition that will start sending current to the motor 40. Thesafety contact element 32 has an upper arm 134 (see FIG. 8) that will bemoved as the nose 34 is pushed into the tool 10, and this upper arm 134will actuate another sensor which, in the illustrated embodiment, is asecond limit switch 132 (see FIG. 8). When both of these actions areoccurring simultaneously, current is delivered to the motor 40 whichwill once again turn the rotary-to-linear lifter 100 a short distance.Also, the controller will energize the solenoid 46, which will rotatethe latch 120 a small angular distance clockwise (as seen in FIG. 5) todisengage the latch catching surface 124 from one of the teeth 92 of thedriver 90. More specifically, this would be the “last” tooth 126 as seenin FIG. 5. Note that FIGS. 6 and 7 show details of the same structuredepicted in FIG. 5 at different perspective angles.

It should be noted that the rotary motion of the lifter 100 will cause asmall upward movement of the driver 90 so that the latch 120 can easilydisengage from the “last” tooth 126 of the driver 90. Thus, there willnot be a binding action that might otherwise cause the mechanism to jam.

Now that all this has occurred, the latch 120 is in its disengagedposition so that its catching surface 124 will not interfere with any ofthe teeth 92 along the right-hand side (as seen in FIG. 5) of the driver90; also the eccentric cam surface 110 is now facing the teeth 92 alongthe left-hand side (as seen in FIG. 5) of the driver 90, and none of thethree “working” pins of the lifter will interfere with those left-handteeth 92. Once the driver tooth “drops off” the last lifting pin 108,the driver 90 is quickly thrust downward in a linear stroke, due to thehigh gas pressure within the main storage chamber 74 and displacementvolume 76. (This is the “gas spring” effect.) Along the way, the driver90 will pick up a fastener that is waiting at the feeder carriage 64,and drive that fastener along the back plate 66 to the exit area at thebottom (at the area 30 on FIG. 1). After this action has occurred, thedriver 90 will be situated at its lower-most position, as viewed in FIG.3.

The pressure of the gas in the combined main storage chamber 74 anddisplacement volume 76 is sufficiently high to quickly force the driver90 downward, and such pneumatic means is typically much faster than anail driving gun that uses exclusively mechanical means (such as aspring) for driving a fastener. This is due to the “gas spring” effectcaused by the high gas pressure within the main storage chamber 74 anddisplacement volume 76 that, once the driver is released, can quicklyand easily move the driver 90 in a downward stroke.

As the driver 90 is being moved downward, the piston 80 and the movablepiston stop 82 are forcing air (or possibly some other gas) out of thecylinder venting chamber 94 that is below the piston. This volume of airis moved through a vent to atmosphere 150, and it is desired that thisbe a low resistance passageway, so as to not further impede the movementof the piston and driver during their downward stroke. The gas above thepiston is not vented to atmosphere, but instead remains within thedisplacement volume 76, which is also in fluidic communication with themain storage chamber 74.

One aspect of the present invention is to provide a rather large storagespace volume to hold the pressurized gas that is also used to drive thepiston downward during a driving stroke of the driver 90. There is afluidic passage 152 between the upper portion of the cylinder and themain storage chamber 74. (In the illustrated first embodiment, thecylinder wall 70 does not extend all the way to the “top” cap 72.) It ispreferred that the volume of the main storage chamber be larger than thetotal volume of the cylinder working spaces (i.e., the displacementvolume) by a volumetric ratio of at least 2.0:1, and more preferably atleast 3.0:1. This will allow for a powerful stroke, and a quick stroke.

The illustrated first embodiment of the present invention allows forboth a quick firing (or driving) stroke time and also a fairly quick“lifting” time to bring the driver back to its upper position, ready forthe next firing (driving) stroke. Both of these mechanical actions cansequentially occur in less than 340 milliseconds (combined time), andallow a user to quickly place fasteners into a surface. In one operatingmode of the present invention, the human user can hold the trigger inthe engaged position and quickly place a fastener at a desired locationmerely by pressing the nose (or “bottom”) of the tool against theworking surface to actuate the fastener driver and place the fastener.Then the user can quickly remove the fastener driver tool from thatsurface, and move it to a second position along the work surface, whilestill depressing the trigger the entire time, and then press the nose(or bottom) of the tool against the working surface at a differentposition, and it will drive a fastener at that “different” position.This is referred to as a “bottom fire” capability, and when using theillustrated embodiment it can occur virtually as fast as a human canplace the tool against a surface, then pick up the tool and accuratelyplace it against the surface at a different position, and thereby repeatthese steps as often as desired until emptying the magazine offasteners. This type of mode of operation will be discussed in greaterdetail below in connection with the logic flow chart starting at FIG.13, with respect to the control system of the fastener driving tool 10.

Referring now to FIG. 8, another side sectional view is provided thatshows some of the elements beneath the latch and other portions of thefirst embodiment fastener driving tool 10. There are twoelectromechanical limit switches 130 and 132. The limit switch 130detects movements of the fourth pin 114 of the rotary-to-linear lifter100 (as noted above). The limit switch 132 detects movement of the upperarm 134, which is a portion of the safety contact element 32 that ispushed rearward (or “up” in these views) with respect to the overalltool 10 when the nose of the tool is pressed against a working surface.These limit switches provide electrical input signals to the controller,which is discussed below in greater detail. It will be understood thatother types of sensors could be used instead of electromechanical limitswitches, such as optoelectrical sensors, or magnetic sensors, includinga Hall-effect switch, or even a metal-sensing proximity switch.

Also viewed on FIG. 8 is a return spring 136, which causes the safetycontact element 32 to be pushed back downward (in this view) once theuser releases the nose of the tool 10 from the working surface. Inaddition, there is a depth of drive adjustment at 138.

Referring now to FIG. 9, further details of the solenoid are viewed. InFIG. 9, the solenoid 140 has a plunger 142 that will move linearlyeither in or out from the main coil body of the solenoid 140. When thesolenoid is energized, it pulls the plunger 142 in toward the solenoidbody 140, which rotates a solenoid arm 146 (part of the solenoid's“linkage”), which in turn rotates the latch shaft 122 that also rotatesthe latch 120 a small arcuate distance. This causes the latch 120 todisengage from the teeth 92 of the driver 90. On the other hand, whenthe solenoid 140 becomes de-energized, the plunger will be pushed out bythe plunger spring 144, which will rotate the solenoid arm 146 a shortdistance, and that in turn rotates the latch shaft 122 and the latch120. This will tend to cause the latch to engage the teeth 92 along theright-hand side (as seen in FIG. 5) of the driver 90. However, sincethis is a spring action, the teeth 92 can slide against the surface ofthe latch 120 and move the latch out of the way if the teeth areattempting to move upward along with the driver 90. However, the springaction of the solenoid plunger spring will be strong enough to push thelatch 120 into its engaged position, and any teeth 92 attempting to movedownward will be caught by the catching surface 124 of the latch 120.

This “catching” action of the latch 120 has more than one benefit. Inthe first place, the latch holds the tooth 126 (which is the “bottomtooth” along the right-hand side of the driver as seen in FIG. 5) inplace when the piston has been lifted to its top or “firing” position.The driver cannot be fired until the latch 120 is moved out of the way,as discussed above. On the other hand, if there is some type of jam oran improper use of the tool by a user such that the driver 90 does nottotally complete its travel during a firing (driving) stroke, the latch120 will also prevent a misfire from occurring at an inconvenient time.

More specifically, if the driver jams during a drive stroke, and if aperson tries to clear the jam, and if there was no precaution taken toprevent the remainder of the stroke from occurring at that moment, thenpossibly an injury could occur when the driver 90 suddenly becomesreleased from its jammed condition. In other words, a fastener could bedriven during the attempt to clear the jam, and that fastener wouldlikely be directed somewhere that is not the original target surface. Inthe present invention, the latch 120 will have its solenoid 140 becomede-energized once the jam occurs (because solenoid 140 will de-energizeafter a “timeout” interval occurs), and therefore the latch 120 will beengaged and the catching surface 124 will be in a position to interferewith the downward movement of the driver teeth 92. By use of thisconfiguration, the driver could only move a short distance even if thejam was suddenly cleared, because the latch catching surface 124 willliterally “catch” the “next” tooth 92 that unexpectedly comes alongduring a downward travel of the driver 90. This makes the tool muchsafer in situations where a complete driver stroke has not occurred.

The process for controlling the solenoid and the moments when thesolenoid will either be energized or de-energized are discussed below inconnection with the flow chart that begins on FIG. 13.

With respect to various types of firing (or driving) modes, a “triggerfire” mode is where the user first presses the tool nose against aworking surface, and then depresses the trigger actuator 54. It is thetrigger being depressed that causes the drive stroke to occur in thissituation. With respect to a “bottom fire” mode, the trigger is actuatedfirst, and then the user presses the nose of the tool against a worksurface, and it is the work surface contact that causes the drive stroketo occur. As discussed above, the user can continue to hold the triggerdown while pressing against and releasing the tool from the work surfacemultiple times, and obtain quick multiple firing strokes (or drivingstrokes), thereby quickly dispensing multiple fasteners into the workingsurface at various locations.

There is also an optional “restrictive firing mode,” in which the noseof the tool must be first placed against a working surface before thetrigger is pulled. If the sequence of events does not unfold in thatmanner, then the drive stroke will not occur at all. This is strictly anoptional mode that is not used by all users, and certainly in not allsituations.

With regard to alternative embodiments of the present invention, anexemplary fastener driving tool can be made with a main storage chambervolume of about twelve cubic inches and a cylinder displacement volumeof about 3.75 cubic inches. This would provide a volumetric ratio of themain storage chamber versus the displacement volume of about 3.2:1. Asdiscussed above, it is desirable for the volumetric ratio of the mainstorage chamber's volume to the displacement volume to be at least2.0:1, and it could be much higher if desired by the fastener drivingtool's designer.

The working pressure in the system could be around 120 PSIG, and shouldprobably be at least 100 PSIG for a quick-firing tool. By the term“working pressure” the inventors are referring to the pressure in thedisplacement volume 76 (and main storage chamber 74) at the time thepiston 80 is at its “ready” position, which is when it is at (orproximal to) its uppermost travel position as illustrated in FIGS. 2-5.

It should be noted that other gases besides air can be used for the mainstorage chamber and the displacement volume, if desired. While air willwork fine in many or most applications, alternative gases could be usedas the “charge gas,” such as carbon dioxide or nitrogen gas. Moreover,the use of nitrogen gas can have other benefits during the manufacturingstage, such as for curing certain adhesives, for example.

In the illustrated first embodiment, there is no fill valve on thefastener driving tool 10 at the storage tank (main storage chamber) 74.This is a preferred mode of the present invention, although an optionalfill valve could be provided, if desired by a tool designer. The designof the preferred mode of the present invention is such that the chargegas should not significantly leak from the tool, and therefore a fillvalve would not be required.

Another feature of the present invention is that a variable stroke ispossible by causing the rotary-to-linear lifter 100 to be rotated amultiple number of times to create a shorter or longer firing (driving)stroke, if desired. In the illustrated first embodiment, the lifter 100makes a complete rotation two times to lift the piston from itslower-most position to its top-most position. This number of rotationsof the lifter could be increased to three times or four times ifdesired, or even could be decreased to a single turn for a shorterstroke tool, if desired.

Another possible variation is to use a composite sleeve for the internalcylinder wall 70, which would make contact with the seals of the piston86. In addition, the outer pressure vessel wall 78 could also be made ofa composite material, if desired. The use of a carbon fiber composite,for example, would decrease weight, but would maintain the desiredstrength.

Referring now to FIG. 10, some of the details of a first pistonarrangement are illustrated in cross-section for one of the embodimentsof the present invention. The piston is depicted at the referencenumeral 80. A piston seal 86 is near the upper end (in this view) of thepiston 80, and a piston scraper 89 is near the lower end (in this view)of the piston. A piston guide ring 88 is located at a central region ofthe piston, and essentially surrounds that middle portion of the piston.

Referring now to FIG. 11, some of the details of a second pistonarrangement are illustrated in cross-section for an alternativeembodiment of the present invention. The second embodiment piston isdesignated by the reference number 180. There are upper and lower sealsat 182 and 184, respectively. Between these seals is an annular space186 that is at least partially filled with lubricating fluid, such asoil. This oil will tend to lubricate the movements of the piston 180along the inner surface of the alternative cylinder wall 170. The seals182 and 184 are designed to hold the oil 188 within the annular space186 indefinitely, or at least to lose the oil only at a very slow rate.

Referring now to FIG. 12, the opposite side (compared to FIGS. 3-5) ofthe rotary-to-linear lifter 100 is illustrated. The three pins 104, 106,and 108 are directly seen in this view, and this is the “working side”of those three pins, which make contact with the teeth 92 of the driver90. FIG. 12 shows the positional relationship of these three pins withrespect to the lifter 100 and the center position for the lifter driveshaft 102, in an exemplary embodiment of the present invention. Inaddition, FIG. 12 shows the semi-circular outer shape of a first part ofthe perimeter of the lifter at 116, and the more elliptical outer shapeof a second part of the perimeter of the lifter at 110, as discussedabove. The outer shape of the perimeter portions (at 110 and 116) definean outer perimeter of a surface from which these pins 104, 106, and 108protrude.

Referring now to FIG. 13, a logic flow chart is provided to show some ofthe important steps used by a system controller for the fastener drivingtool 10 of the illustrated embodiment for the present invention.Starting at an initializing step 200, a step 202 loads registers withpredetermined values, and a step 204 loads special function registerswith predetermined values. A step 206 now “checks” the RAM (RandomAccess Memory) to be sure it is functioning properly, and then a step208 clears the RAM. A step 210 now loads unused RAM with predeterminedvalues, based on the software coding for the system controller(typically in firmware or hard-coded).

A step 212 now determines the stability of the system electrical powersupply. And then a step 214 initializes the interrupts that will be usedfor the controller. The controller is now ready to enter into anoperational routine.

At a step 220, the control logic enters a “FIRST 1” routine. A decisionstep 240 now determines whether or not a “mode” selector switch has beenactivated. (Note, this mode switch would typically be only an optionalfeature for a driving tool 10, and many tools will not include this modeswitch at all.) If the answer is NO, then the logic flow is directed toa decision step 222. On the other hand, if the mode selector switch wasturned “on,” then the logic flow is directed to a step 242 in which thetool enters a “restrictive fire” routine. The logic flow is directed nowto a decision step 244 that determines if the trigger has been pulled.If the answer is NO, then the logic flow is directed to a decision step224. On the other hand, if the trigger has been pulled, then the logicflow is directed to a step 246 that will further direct the logic flowto the “STOP 1” function (or routine) at step 380 on FIG. 15. It shouldbe noted that, in the “restrictive fire” mode of operation, the triggercannot be pulled first; instead the nose of the fastener driving toolmust be pushed against the solid surface before the trigger is pulled.

If the answer at step 240 was NO, the decision step 222 now determineswhether or not the trigger has been pulled. If the answer is YES, thelogic flow is directed to a step 230 in which the logic flow enters a“TRIGGER” routine. A step 231 turns on a “work light” which is a smallelectric lamp (e.g., an LED) that illuminates the workpiece where thefastener is to be driven.

A decision step 232 now determines whether or not a predeterminedtimeout has occurred, and if the answer is YES, a step 234 directs thelogic flow to a “STOP 1” routine, that is illustrated on FIG. 15 at astep 380. What this actually means is that a user pulled the trigger,but then did not actually use the tool against a solid surface, andrather than having the tool ready and primed to fire a fastener at anymoment for an indefinite period of time, a predetermined amount of timewill pass (i.e., the “timeout” interval), and once that has occurred,the system will be basically deactivated in the STOP 1 mode. This is nota permanent stoppage of the functioning of the tool, but is onlytemporary. Note that the “timeouts” are interrupt driven, in anexemplary embodiment of the present invention.

If the timeout has not occurred at decision step 232, then a decisionstep 236 determines if the safety has been actuated. If the answer isNO, then the logic flow is directed back to the FIRST 1 routine 220. Onthe other hand, if the safety has been actuated at step 236, then thelogic flow is directed to a step 238 that will send the logic flow to a“DRIVE” routine, which is on FIG. 14 at a step 260. This will bediscussed below in greater detail.

If, either at step 222 or step 244, the trigger was not yet pulled, thenthe logic flow is directed to the decision step 224. When the logic flowreaches decision step 224, the logic now determines whether or not thesafety has been actuated. This step determines whether or not the safetycontact element 32 has been pressed against a solid object to an extentthat actuates the sensor (e.g., limit switch 132), which means that thetool is now pressed against a surface where the user intends to place afastener. If the answer is NO, the logic flow is directed back to themode switch query at decision step 240. However, if the answer is YES,the logic flow is directed to a step 250 in which the controller entersa “SAFETY” routine.

Once at the SAFETY routine at step 250, a step 251 turns on the “worklight,” which is the same lamp/LED that was discussed above in referenceto step 231. A decision step 252 now determines whether or not a timeouthas occurred, and if the answer is YES, the logic flow is directed to astep 254 that directs the logic flow to the “STOP 1” function at step380 on FIG. 15. This temporarily stops the tool from operating. On theother hand, if the timeout has not yet occurred, the logic flow isdirected to a decision step 256 that determines whether the trigger hasbeen pulled. If the answer is NO, the logic flow is directed back to thedecision step 224. On the other hand, if the answer is YES, the logicflow is directed to a step 258 that causes the tool to enter the “DRIVE”mode of operation at step 260 on FIG. 14.

As can be seen by reviewing the flow chart of FIG. 13, unless the tool10 is in the restrictive fire mode (at step 242), the tool can beactuated with either one of the two important triggering steps occurringfirst: i.e., the trigger could be pulled before the safety is actuated,or vice versa.

Referring now to FIG. 14, the logic flow from FIG. 13 is directed to the“DRIVE” routine 260 from two other steps on FIG. 13: these are step 238and step 258. Once at the DRIVE routine 260, a switch debounce step 262is executed to determine whether or not one or both of the triggeringelements was somehow only actuated intermittently. If so, the systemdesigners have determined that the tool should not operate until it ismore certain that the input switches have actually been actuated. To dothis, the logic flow is directed to a decision step 264 to determine ifthe safety is still actuated. If the answer is NO, then the logic flowis directed to a step 266 that sends the logic flow back to the SAFETYroutine at step 250. On the other hand, if the safety still is actuatedat step 264, then the logic flow is directed to a decision step 270 todetermine if the trigger is still being pulled. If the answer is NO,then the logic flow is directed to a step 272 that sends the logic flowback to the TRIGGER routine at step 230.

On the other hand, if decision steps 264 and 270 are both answeredaffirmatively, then a step 280 clears the operational timers, and thelogic flow is then directed to a decision step 282 that determines ifthe software code flow is within certain parameters. This is afault-checking mode of the software itself, and if the system does notdetermine a satisfactory result, then the logic flow is directed to astep 284 that sends the logic flow to a “STOP” routine at a step 370 onFIG. 15. This will ultimately turn the tool off and require a safetyinspection of the tool, or at least have the tool reset. However, thetool does not need to be completely disabled, and after the safetyinspection and tool reset procedure, the tool will be ready to use againwithout being sent to a service center. In an exemplary mode of theinvention, the code flow check step determines if a correct numberresides in a register or memory location; this number is the result ofbeing incremented at predetermined executable steps of the software forthe system controller.

If the software code flow check is within acceptable parameters atdecision step 282, then the logic flow is directed to a step 290 thatturns on the motor, and then a step 292 that turns on the solenoid. Astep 294 now starts the solenoid timer and a step 296 now starts themotor run timer. As will be discussed below, these timers will beperiodically checked by the system controller to make sure that certainthings have occurred while the solenoid is on and while the motor isrunning. Otherwise, after a predetermined maximum amount of time, themotor will be turned off and the solenoid will be turned off due tothese timers actually timing out, which should not occur if the tool isbeing used in a normal operation, and if the tool is functioningnormally.

In addition to the solenoid and motor run timers discussed above, a“dwell timer” is used to allow the tool to begin its normal operationbefore any further conditions are checked. This is accomplished by adecision step 298 on FIG. 14, which causes the logic flow to essentiallywait a short amount of time before continuing to the next logic steps.

Once the dwell timer has finished at step 298, the logic flow isdirected to a decision step 300 that determines if the solenoid “ontime” has been exceeded. If the answer is YES, the logic flow isdirected to a step 302 that turns off the solenoid. This situation doesnot necessarily mean the tool is being misused or is not functioningproperly, and therefore the logic flow does not travel to a “stop step”from the step 302. Instead, the logic flow is directed to a decisionstep 304, discussed below.

If the solenoid on time has not been exceeded, then the logic flow alsois directed to the decision step 304, which determines if the cam limitswitch has received a first signal. This is the limit switch 130 thatdetects the presence or absence of the fourth pin 114 of the lifter. Ifthe tool of the illustrated embodiment is being used, the lifter 110will make two complete rotations when lifting the driver and piston fromtheir bottom-most positions to their top-most positions. Therefore, thecam limit switch 130 will receive two different signals during thislift. Step 304 determines if the first signal has occurred. If not, thena decision step 310 determines whether the motor timeout has occurred.If the answer is NO, then the logic flow is directed back to decisionstep 300. On the other hand, if the motor run timer has indeed timedout, then the logic flow is directed to a step 312 that sends the logicflow to a “STOP” routine at step 370. This would likely indicate thatthere is a problem with the tool, or a problem with the way the user isattempting to operate the tool.

Referring back to decision step 304, if the first signal from the camhas occurred, then the logic flow is directed to a step 306 that turnsoff the solenoid. This will allow the latch 120 to engage the teeth 92of the driver 90, in case there has been some type of jam, or other typeof unusual operation while the driver and piston are being lifted. Italso allows the latch 120 eventually to properly engage the bottom-mosttooth 126 of the driver, which is the normal operation once the driverand piston have been raised to their top-most (or firing) position.

The logic flow is now directed to a decision step 320 that determineswhether a second signal has been received from the cam limit switch. Ifthe answer is NO, then the logic flow is directed to a decision step 322that determines whether or not the motor run timer has timed out. If theanswer is NO, then the logic flow is directed back to decision step 320.On the other hand, if the motor timer has timed out, the logic flow isdirected to a step 324 that directs the logic flow to the “STOP” routineat 370, and indicates that there is some type of problem.

Once decision step 320 determines that the second signal from the camhas been received, then the logic flow is directed to a step 330 thatturns off the motor, then to a step 332 that starts a “reset” timeoutreferred to as “all switches on.” In this mode, it is either assumedthat both the actuation (input) devices are still actuated, or at leastthat the controller needs to make an examination of those input devicesto see what the proper status of the tool should be. Accordingly, thelogic flow is directed to a decision step 340 that determines if thesafety is still actuated. If the answer is NO, then the logic flow isdirected to a step 342 that then sends the logic flow to the “FIRST 1”routine at step 220 on FIG. 13. On the other hand if the safety is stillactuated, the logic flow is directed to a decision step 350 thatdetermines if the trigger is still pulled. If the answer is NO, then thelogic flow is directed to a step 352 that also directs the logic flow tothe “FIRST 1” step at 220 on FIG. 13. Finally, if the trigger is stillpulled, then a decision step 360 determines whether or not a “reset”timeout has occurred, and if the answer is YES, the logic flow isdirected to a step 362 that sends the logic flow to the “STOP 1” routineat step 380 on FIG. 15. If the reset timeout has not yet occurred atstep 360, then the logic flow is directed back to the decision step 340and the inspection of all of the switches will again be performed.

The logic flow is continued on FIG. 15, in which there are two differenttypes of stop routines. The routine called “STOP” at step 370 will firstturn off the motor at a step 372, turn off the solenoid at a step 374,and turn off the work light at a step 376. The STOP routine will thenclear the timers at a step 378. The logic flow then becomes a “DO-Loop,”and continues back to the STOP routine at step 370. This is a faultmode, and the tool must be inspected. As a minimum, it needs to be resetto terminate the DO-Loop processing of the software, which means thatthe battery must be disconnected from the tool. If the user has beenusing the tool properly, this may be an indication that there is someoperational problem with the tool itself, or that a fastener perhaps hasjammed somewhere in the tool and the operator did not notice that fact.

The other type of STOP routine is the “STOP 1” routine at step 380. Oncethat occurs, a step 382 turns off the motor, turn off the solenoid at astep 384, and turn off the work light at a step 386. The STOP 1 routinewill then clear the timers at a step 388, and a decision step 390determines whether or not the trigger is still pulled. If the answer isYES, then the logic flow is directed back to the STOP 1 routine at step380. If the trigger is not pulled at step 390, the logic flow is thendirected to a decision step 392 that determines if the safety is stillactuated. If YES, the logic flow is directed back to the STOP 1 routineat step 380. However, if the safety is not actuated, the logic flow isdirected to a step 398 that sends the logic flow to the “FIRST 1”routine at step 220 on FIG. 13. At this point, the tool has beensuccessfully used, and is ready for the next firing (driving) actuation.

Referring now to FIG. 16, a second embodiment of a fastener driving toolis generally designated by the reference numeral 401. Tool 401 is mainlydesigned to linearly drive fasteners such as nails and staples. Tool 401includes a handle portion 403, a fastener driver portion 405, a fastenermagazine portion 407, and a fastener exit portion 409.

A “right” outer cover or “housing” of the driver portion is indicated at411. A “top” cover is indicated at 412, while a “front” outer cover ofthe driver portion is indicated at 413. A “rear” cover for the handleportion is indicated at 415 (which is also the battery pack cover),while a “rear” cover of the magazine portion is indicated at 416. Itwill be understood that the various directional nomenclature providedabove is with respect to the illustration of FIG. 16, and the secondembodiment fastener driving tool 401 can be used in many other angularpositions, without departing from the principles of the presentinvention.

The area of the second embodiment tool 401 in which a fastener isreleased is indicated approximately by the reference numeral 417, whichis the “bottom” of the fastener exit portion of tool 401. Before thetool is actuated, a safety contact element 418 extends beyond the bottom417 of the fastener exit, and this extension of the safety contactelement is depicted at 419, which is the bottom or “front” portion ofthe safety contact element. Other elements that are depicted in FIG. 16include an upper guide body 421 and a front cover 423; the upper guidebody generally is in mechanical communication with the magazine portion407.

Reference numeral 445 indicates a magazine housing, while referencenumeral 447 indicates a fastener track through which the individualfasteners run while they remain within the magazine portion 407. Afeeder carriage 448 (see FIG. 18) is used to feed an individual fastenerfrom the magazine into the drive mechanism area, and a back plate 449 isused to carry an individual fastener while it is being driven. In theillustrated embodiment, the feeder carriage 448 positions a fastener toa position within the upper guide body 421 that is coincident with thepath of the driver member 490 (see FIG. 20), so that when the driver 490moves through a driving stroke, its driving end will basically interceptthe fastener and carry that fastener to the exit end of the tool 401,essentially at the bottom portion 417 of the tool's exit area.

The second embodiment fastener driving tool 401 also includes a motor427 (see FIG. 17) which acts as a prime mover for the tool, and whichhas an output that drives a gearbox 428 (see FIG. 17). An output shaft429 (see FIG. 17) of the gearbox drives a lifter drive shaft 402 (seeFIG. 27). A solenoid 431 (see FIG. 17) is included in tool 401, andfurther details of its operation are discussed below. A battery 433 isattached near the rear of the handle portion 403, and this batteryprovides electrical power for the motor 427 as well as for a controlsystem.

A printed circuit board (see FIG. 17) that contains a controller isgenerally designated by the reference numeral 435, and is placed withinthe handle portion 403 in this embodiment. A trigger switch 437 (seeFIG. 17) is activated by a trigger actuator 439. As can been seen byviewing FIG. 16, the handle portion 403 is designed for gripping by ahuman hand, and the trigger actuator 439 is designed for linearactuation by a person's finger while gripping the handle portion 403.Trigger switch 437 provides an input to the control system 435.

A three-position selector switch, acting as a “mode” control switch, ismounted on tool 401 at 441. This switch 441 allows the user (the tool'soperator) to select an operating “Mode A” or an operating “Mode B”, orto turn the tool OFF. These operating modes are described in detailbelow, and in conjunction with logic flow charts in the drawings.

There also are one or more light-emitting diodes (LEDs) 443 mounted ontool 401, which provides an indication as to certain functions of thetool. This is described below in greater detail, in the description ofthe logic flow charts. There are also other input devices for thecontroller, however those input devices are not seen in FIG. 16.

The controller at 435 will typically include a microprocessor or amicrocomputer device that acts as a processing circuit. At least onememory circuit will also typically be part of the controller, includingRandom Access Memory (RAM) and Read Only Memory (ROM) devices. To storeuser-inputted information (if applicable for a particular tool model), anon-volatile memory device would typically be included, such as EEPROM,NVRAM, or a Flash memory device.

Referring now to FIGS. 19 and 20 (which are similar to FIGS. 2 and 3), aworking cylinder subassembly is designated by the reference numeral 453,and this is included as part of the fastener driver portion 405. Theworking cylinder 453 includes a cylinder wall 451, and within thiscylinder wall 451 is a movable piston 458. Further details of thispiston arrangement are illustrated in FIG. 28, described below.Surrounding the cylinder wall 451, in the illustrated second embodiment,is a main storage chamber 454 (also sometimes referred to herein as a“pressure vessel storage space”) and an outer pressure vessel wall 456(which corresponds to the “front” cover 413 of FIG. 16, along the rightportion of this view). At the top (as seen in these views) of thefastener driver portion 405 is an upper end portion at 455 for thecylinder mechanism.

Also within the fastener driver portion 405 are mechanisms that willactually drive a fastener into a solid object. This includes a driver490, a cylinder “venting chamber” 492 beneath the piston 458 (whichwould typically always be at atmospheric pressure), a driver track (notseen in this view; however, see FIG. 21 at 494), a rotary-to-linearlifter 400, and a latch 420. The driver 490 is also sometimes referredto herein as a “driver member” and the rotary-to-lifter 400 is alsosometimes referred to herein as a “lifter member,” or simply as a“lifter.” Driver 490 is rather elongated, and as an individual elementcan best be seen in FIGS. 23 and 24. There are multiple “teeth” 491 thatare positioned along the driver. In the illustrated embodiment, theseteeth 491 are spaced-apart not only in a transverse direction from theelongated centerline of driver 490, but they are also spaced-apart fromone another along the outer longitudinal edges of the driver 490. Thepositions of teeth 491 are clearly illustrated in FIG. 24.

It will be understood that the precise positions for the teeth 92 and491 could be different from those illustrated for the driver 90 or 490,without departing from the principles of the present invention. It willalso be understood that the precise shapes of teeth 92 and 491 could bedifferent from those illustrated for the driver 90 or 490, withoutdeparting from the principles of the present invention. It will befurther understood that the longitudinal edges of the driver elements 90and 490 do not necessarily have to be linear or straight, although astraight edge is probably the simplest to construct and use. Moreover,the longitudinal edges of the driver elements 90 and 490 do notnecessarily need to be parallel to one another, or parallel to thelongitudinal axis of the driver itself, although again, such parallelconstruction is probably the simplest to build and use.

There is a cylinder base 493 that mainly separates the gas pressureportions of the fastener driver portion 405 from the mechanical portionsof that driver portion 405. The venting of air from the cylinder ventingchamber 492 passes through the cylinder base 493, as seen at a vent 450on FIG. 20. The mechanical portions of FIG. 20 begin with arotary-to-linear lifter 400 which was briefly mentioned above, alongwith a lifter drive shaft 402. Drive shaft 402 protrudes through thecenter portions of the fastener driver portion 405 and through thecenter of the lifter 400, and this shaft is used to rotate the lifter,as desired by the control system. (See also FIG. 27.)

Lifter 400 can be designed with an entirely circular outer perimeter, orit can have a different shape. In the first embodiment of FIGS. 1-12,lifter 100 was arcuate and portions of its perimeter exhibited aneccentric shape of a cam (see FIG. 2). A portion of the lifter's outerperimeter was mainly circular for about half of a circle (designated bythe reference numeral 116), but the other half of the lifter's outerperimeter was more eccentric, which provided an elliptical surface(designated by the reference numeral 110). In the second embodiment ofFIGS. 16-29, the outer shape of lifter 400 is still illustrated ashalf-circular and half-eccentric. However, it will be understood thatthe lifter's exact outer shape is not important, so long as it providesa base to hold in place certain protrusions (or “pins”) that will makephysical contact with teeth on the driver 490, but in a manner thatcreates a discontinuous contact surface with those teeth. This will bediscussed below in greater detail. (See, for Example, FIGS. 30-33.)

The rotary-to-linear lifter 400 includes three cylindrical protrusions(or “extensions”) that will also be referred to herein as “pins.” Thefirst such pin (“pin 1”) is designated 404, the second pin (“pin 2”) isdesignated 406, while the third pin (“pin 3”) is designated 408. (See,FIG. 29.) These pins are mainly not visible on FIG. 19, since they faceaway from the viewer of this FIG. 19.

It should be noted that FIGS. 19 and 20 do not show a “boss portion” ofthe three pins 404, 406, and 408, (as did pins 104, 106, and 108 on FIG.3), since such boss portions of the pins 404, 406, 408 are not entirelynecessary for the proper functioning of the rotary-to-linear lifter 400.Instead, the surface of the lifter 400 may be perfectly smooth (e.g.,flat) at those locations rather than exhibiting a “boss.”

It should be understood that the “working side” of these three pins 404,406, and 408 is on the opposite side of the lifter 400 in the view ofFIG. 20. When discussing these pins 404, 406, and 408 with respect toFIG. 20 in this written description, it is with reference to thenon-protruding side of those pins; however, the effects of the “workingside” of those pins is discussed in some detail with respect to otherstructures that are also illustrated on FIGS. 20-25.

It should also be noted that pins 404, 406, an 408 are illustrated ashaving circular cross-sectional shapes, which is desirable for thisembodiment, although other cross-sectional shapes could instead be usedwithout departing from the principles of the present invention. Forexample, the pins could have a smooth arcuate outer surface along theportions that will come into contact with the protrusions or “teeth” ofthe lifter 490, and the remaining portion of the outer surface of thepins could exhibit a sharp angular cut-off edge, that for example, wouldhave the appearance of a slice of pie. This alternative shape can applyboth to the pins 104, 106, and 108 of the first embodiment and to thepins 404, 406, and 408 of the second embodiment, without departing fromthe principles of the present invention. Moreover, the pins do notnecessarily need to protrude from the lifter surface at right angles.

In the first embodiment of FIGS. 1-12, there was a fourth cylindricalpin (“pin 4”) that protruded from the opposite side of the lifter 100,designated pin 114. In this second embodiment of FIGS. 16-29, there isno fourth pin at all. Instead a small permanent magnet at 414 is placedin the lifter 400. A Hall effect sensor (described below) is used tosense the movements of this magnet 414, and thus the movements of lifter400.

The latch 420 that was briefly noted above is depicted on FIG. 20, andhas a latch shaft 422 protruding therethrough, and this shaft rotatesthe latch 420 as determined by the controller. Latch 420 includes alatch “catching surface” at 424 (see FIG. 22), and this will be morefully explained below.

In FIG. 19, the piston 458 depicted at or near its uppermost or top-mostposition (in this view), and a gas pressure chamber 457 can be seenabove the top-most area of the piston, near the top piston seal 482 (seeFIG. 28). It will be understood that the gas pressure chamber 457 andthe main storage chamber (or storage space) 454 are in fluidiccommunication with one another. It will also be understood that theportion to the interior of the cylinder wall 451 forms a displacementvolume that is created by the stroke of the piston 458. In other words,the gas pressure chamber 457 is not a fixed volume, but this chamberwill vary in volume as the piston 458 moves up and down (as seen inFIGS. 19 and 20). As noted above, this type of mechanical arrangement isoften referred to as a “displacement volume,” and that terminology willmainly be used herein for this non-fixed volume 457.

In FIG. 20, the piston 458 is piston is depicted at or near itsbottom-most travel position (in this view), and a gas pressure chamber457 can be seen above the top-most area of the piston. It will beunderstood that the gas pressure chamber 457 and the main storagechamber (or storage space) 454 are in fluidic communication with oneanother. It will also be understood that the portion to the interior ofthe cylinder wall 451 forms a displacement volume that is created by thestroke of the piston 458. In other words, the gas pressure chamber 457is not a fixed volume, but this chamber will vary in volume as thepiston 458 moves up and down. This type of mechanical arrangement isoften referred to as a “displacement volume,” and that terminology willmainly be used herein for this non-fixed volume 457.

It will be further understood that the main storage chamber 454preferably comprises a fixed volume, which typically would make it lessexpensive to manufacture; however, it is not an absolute requirementthat the main storage chamber actually be of a fixed volume. It would bepossible to allow a portion of this chamber 454 to deform in size and/orshape so that the size of its volume would actually change, duringoperation of the present invention, without departing from theprinciples of the present invention.

In the illustrated embodiment for the second embodiment fastener drivingtool 401, the main storage chamber 454 substantially surrounds theworking cylinder 453. Moreover, the main storage chamber 454 is annularin shape, and it is basically co-axial with the cylinder 453. This is apreferred configuration of the illustrated second embodiment, but itwill be understood that alternative physical arrangements could bedesigned without departing from the principles of the present invention.

For example, FIG. 34 illustrates a fastener driver mechanism 714 inwhich a main storage chamber 774 is not co-axial with a working cylinder771 of the fastener driving tool, which is generally designated by thereference numeral 710. In other words, storage chamber 774 does notsubstantially surround the working cylinder 771, and instead is locatedoff to one side of this working cylinder. This arrangement allows forvarious physical component arrangements of the tool 710, and offers adifferent possible center of mass, which might be advantageous for somespecial applications.

In FIG. 34, the main storage chamber 774 has an outer pressure vesselwall 778, and the working cylinder 771 has a cylinder wall 770. Thesetwo spaces 774 and 771 are pneumatically in communication with oneanother by way of a passageway 752, near the top (in this view) of theworking cylinder, at 772. Within cylinder wall 770 is a movable piston780 (not visible in this view), which can be constructed in a similarmanner to the movable piston 458 illustrated in FIG. 28, describedabove. Also within the fastener driver portion 714 is a driver member790 (not visible in this view), which can be constructed in a similarmanner to the driver 490 illustrated in FIGS. 23 and 24, and describedabove.

A cylinder base 796 separates the gas pressure portions of the fastenerdriver portion 714 from the mechanical portions of that fastener driverportion 714. The tool 710 can include a handle portion (not shown), afastener magazine portion 407 (not shown), and a fastener exit portion718. The remaining parts of tool 710 can be very similar, or identical,to other parts of the second embodiment tool 401, illustrated in FIGS.16-29.

Referring again to FIG. 20, the piston 458 is depicted near or at itsbottom-most travel position, and in this configuration, the displacementvolume 457 and the main storage chamber 454 are at their largestcombined volumes, while the cylinder venting chamber 492 is at itsminimum volume. This bottom position is also sometimes referred toherein as the “driven position.” In FIG. 20, movable piston 458 is nowin contact with the stationary piston stop 463, which is why thecylinder venting chamber 492 is at its minimum (or zero) volume. In FIG.20, the driver 490 is also at its bottom-most travel position, and itslower-most tip can be seen extending out the exit port at the bottom ofa lower guide body 425.

In FIG. 20, the rotary-to-linear lifter 400 and the latch 420 are intheir respective positions at the end of a firing (driving) stroke, andthe latch 420 has its latching surface 424 in a location that will notinterfere with the teeth 491 of the driver 490. This is necessary sothat the driver 490 can make a driving stroke from its top-most positionto its bottom-most position (see also, FIG. 22). However, the latch 420will later be slightly rotated by the latch shaft 422 (which isspring-loaded) so that its catching surface 424 will be able tointerfere with the teeth 491.

In the configuration depicted on FIG. 20, the fastener driving tool 401has been used to drive a fastener, and the tool now must cause thedriver 490 to be “lifted” back to its top-most position for a new firing(driving) stroke. This is accomplished by rotating the lifter 400, whichis actuated by the motor 427, through its gearbox 428, etc.

As rotary-to-linear lifter 400 rotates counterclockwise (as seen in FIG.20) at least one of its pins 404, 406, or 408 will come into contactwith one of the teeth 491 along the left side (as seen in FIG. 20) ofthe driver 490. This will cause the driver 490 to be “lifted” upward (asseen in FIG. 20) in a “return” stroke. As the lifter 400 rotates, one ofthe teeth 491 will be in contact with one of the rotating pins 404, 406,408 throughout a portion of the rotational travel of the lifter, and the“next” pin will then come into contact with the “next” tooth 491 so thatthe driver 490 continues to be moved upward. This lifting procedure willcontinue until the controller determines that the driver has been movedto its proper position for a new driving stroke. When this occurs, thelatch 420, which is spring-loaded, will have its latch catching surface424 in a proper location to “catch” the closest tooth 491 along theright-hand side (as seen in FIG. 20) of the driver 490, therebypreventing the driver from falling downward for any significantdistance. After this occurs, the “next” lifter pin (which will be thepin 404) will then come along and again make contact with one of theteeth 491 along the left-hand side (as seen in FIG. 20) of the driver490, thereby continuing to lift the driver toward the top (as seen inFIG. 20) of the cylinder 453.

In the illustrated embodiment of the second embodiment fastener drivingtool 401, the rotary-to-linear lifter 400 makes two complete rotationsto lift the driver 490 from its bottom-most position to its top-mostposition. (The upper position is also sometimes referred to herein asthe “ready position.”) At the end of the second rotation, the parts willbe configured as illustrated in FIG. 21. The piston 458 will again benear the top of the cylinder 453, and the combined volumes of the mainstorage chamber 454 and displacement volume 457 have now been reduced toa smaller volume, which means their gases are under a greater pressure,since the gas that was above the piston and in chamber 454 wascompressed during the lift of the driver. (As noted above, the actualvolume of the main storage chamber 454 does not change in theillustrated embodiment.) During the lift of the driver, the latch 420was “engaged” with the teeth 491, however, the latch has a smoothsurface in one direction that allows the teeth 491 to push the latch outof the way during the upward lift of the driver. This is much like aratchet-type action, remembering that the latch is spring-loaded (andthus has a mechanical bias) so as to act in this manner.

At the end of the piston's normal upward movement, the “last” toothalong the right-hand side (as best seen in FIG. 23) of the driver 490 isengaged with the latch catching surface 424, and so latch 420 nowprevents the driver from being moved downward (as seen in this view).(This is similar to the arrangement of components depicted in FIG. 4,for the first embodiment.) The third pin 408 is still in contact withthe lower-most tooth 491 along the left-hand side of the driver 490, atthis point in the rotational travel of the rotary-to-linear lifter 400.There is a sensor which, in the illustrated embodiment, is a Hall effectsensor 430 (see FIG. 25) that detects the rotational movements of thelifter 400. This sensor detects the magnet 414, as discussed below ingreater detail.

When the sensor 430 detects the magnet 414 a first time (in this secondembodiment), the control system turns off the solenoid 431, which willthen allow the latch 420 to engage the right-hand teeth (in these views)of the lifter 400. Note that the solenoid can also be turned off earlierduring the lift, if desired. When sensor 430 detects this magnet 414 asecond time (in the second embodiment), the current to the motor 427 isturned off, and the motor thus is de-energized and stops the liftingaction of the driver 490. As described herein, the solenoid 431 acts asa latch actuator.

In the second illustrated embodiment tool 401, the latch surface 424 isnot in contact with the driver teeth 491 when the driver 490 has beenmoved to its “ready” position. In this second illustrated embodiment,the gearbox 428 has an attribute by which it essentially is self-lockingfrom its output side (i.e., from its output shaft 429), and thisprevents the lifter 400 from allowing the driver 490 to move “backward,”which is the “down” direction in FIG. 21. Therefore, the driver/pistonsubassembly will not drift downward a small distance, and thus, thedriver teeth 491 do not come into contact with the latch, even in viewof the gas pressure above piston 458 (in the space 457).

At the “ready” position for the driver 490, the latch 420 may bepositioned such that it would interfere with the driver teeth 491 (i.e.,in an “interfering position”) as a safety feature (i.e., in which thelatch surface 424 would “catch” the teeth 491 of the driver 490, if thedriver somehow would move downward). However, the gearbox/liftercombination does not allow the “last tooth” 426 to contact that latch420 at this point in the tool's operation.

This is the position illustrated in FIG. 21 of the second embodimenttool, and this configuration is considered to be the “rest” position ofthe tool 401. Although the gas pressure in the combined main storagechamber 454 and displacement volume 457 is at its maximum, the gearboxprevents the driver 490 from being moved further downward (in thisview), so the piston/driver combination is essentially locked in thisposition until something else occurs. In a preferred mode of theinvention, the pressure vessel may be pressurized at about 130 PSIG to140 PSIG, just before a driving stroke.

It should be noted that, for the second embodiment tool 401, the gearboxcan be of yet another alternative construction. For example, instead ofbeing self-locking from its output side, a “regular” gearbox could beused if provided with a “one-way” feature, such as an adjacent one-wayclutch (or a one-way clutch constructed therewithin). In this manner,the driver 490 would still be prevented from moving down (in FIG. 21)and contacting the latch surface 424, just before a driving stroke.

When it is time to drive a fastener, the next action in the illustratedsecond embodiment is to cause the motor 427 to become energized onceagain, so that the lifter 400 rotates further in its original direction.This occurs by two independent actions by the user: in some modes of theinvention, these two independent actions can occur in either order.(There is also an optional “restrictive mode” of operation, in which thetwo independent actions must occur in a specific order.) These twoactions are: pressing the nose 419 of the safety contact element 418against a solid surface, and depressing the trigger actuator 439. Thetrigger actuator will cause the trigger switch 437 to change state,which is one condition that will start sending current to the motor 427.The safety contact element 418 has an upper arm 434 (see FIG. 25) thatwill be moved as the nose 419 is pushed into the tool 401, and thisupper arm 434 will actuate another sensor which, in the illustratedembodiment, is a small limit switch 432 (see FIG. 25).

When both of these actions occur simultaneously, current is delivered tothe motor 427 which will once again turn the rotary-to-linear lifter 400a short distance. Also, the controller energizes the solenoid 431, whichrotates the latch 420 a small angular distance clockwise (as seen inFIG. 20) to move the latch catching surface 424 from an interferingposition, so that the latch will not prevent the driver 490 from movingdownward when it is correctly time for a driving stroke. Therefore, the“last” tooth 426 of driver 490 (as seen in FIGS. 21 and 22) would not“catch” on this latch catching surface. Note that FIGS. 23 and 24 showdetails of the same structure depicted in FIG. 22 at differentperspective angles.

Now that all this has occurred, the latch 420 is in its disengagedposition so that its catching surface 424 will not interfere with any ofthe teeth 491 along the right-hand side (as seen in FIG. 20) of thedriver 490; and none of the three “working” pins of the lifter 400 willinterfere with those left-hand teeth 491. Once the driver tooth 491“drops off” the last lifting pin 408, the driver 490 is quickly thrustdownward in a driving stroke, due to the high gas pressure within themain storage chamber 454 and displacement volume 457. (This is the “gasspring” effect.) Along the way, the driver 490 will pick up a fastenerthat is waiting at the feeder carriage 448, and drive that fasteneralong the back plate 449 to the exit area at the bottom (at the area 417on FIG. 16). After this action has occurred, the driver 490 will besituated at its lower-most position, as viewed in FIG. 20.

The pressure of the gas in the combined main storage chamber 454 anddisplacement volume 457 is sufficiently high to quickly force the driver490 downward, and such pneumatic means is typically much faster than anail driving gun that uses exclusively mechanical means (such as aspring) for driving a fastener. This is due to the “gas spring” effectcaused by the high gas pressure within the main storage chamber 454 anddisplacement volume 457 that, once the driver is released, can quicklyand easily move the driver 490 in a downward stroke.

As the driver 490 is being moved downward, the piston 458 and themovable piston stop 459 are forcing air (or possibly some other gas) outof the cylinder venting chamber 492 that is below the piston. Thisvolume of air is moved through a vent to atmosphere 450, and it isdesired that this be a low resistance passageway, so as to not furtherimpede the movement of the piston and driver during their downwardstroke. The gas above the piston is not vented to atmosphere, butinstead remains within the displacement volume 457, which is also influidic communication with the main storage chamber 454.

One aspect of the present invention is to provide a rather large storagespace or volume to hold the pressurized gas that is also used to drivethe piston downward during a driving stroke of the driver 490. There isa fluidic passage 452 between the upper portion of the cylinder and themain storage chamber 454. (In the illustrated second embodiment, thecylinder wall 451 does not extend all the way to the top end region455.) It is preferred that the volume of the main storage chamber belarger than the total volume of the cylinder working spaces (i.e., thedisplacement volume) by a volumetric ratio of at least 2.0:1, and morepreferably at least 3.0:1. This will allow for a powerful stroke, and aquick stroke; moreover, it provides for an efficient operating airspring.

The illustrated second embodiment of the present invention allows forboth a quick firing (or driving) stroke time and also a fairly quick“lifting” time to bring the driver back to its upper position, ready forthe next firing (driving) stroke. Both of these mechanical actions cansequentially occur in less than 340 milliseconds (combined time), andallow a user to quickly place fasteners into a surface. In one operatingmode of the present invention, the human user can hold the trigger inthe engaged position and quickly place a fastener at a desired locationmerely by pressing the nose (or “bottom”) of the tool against theworking surface to actuate the fastener driver and place the fastener.Then the user can quickly remove the fastener driver tool from thatsurface, and move it to a second position along the work surface, whilestill depressing the trigger the entire time, and then press the nose(or bottom) of the tool against the working surface at a differentposition, and it will drive a fastener at that “different” position.This is referred to as a “bottom fire” capability, and when using theillustrated embodiment it can occur virtually as fast as a human canplace the tool against a surface, then pick up the tool and accuratelyplace it against the surface at a different position, and thereby repeatthese steps as often as desired until emptying the magazine offasteners. This type of mode of operation will be discussed in greaterdetail below in connection with the logic flow chart starting at FIG.35, with respect to the control system of the fastener driving tool 401.

Referring now to FIG. 25, another side sectional view is provided thatshows some of the elements beneath the latch and other portions of thesecond embodiment fastener driving tool 401. There are two limitswitches 430 and 432. The limit switch 430 is a Hall-effect sensor thatdetects movements of the magnet 414 of the rotary-to-linear lifter 400(as noted above). The limit switch 432 is a small electromechanicallimit switch that detects movement of the upper arm 434, which is aportion of the safety contact element 418 that is pushed rearward (or“up” in these views) with respect to the overall tool 401 when the noseof the tool is pressed against a working surface. These limit switchesprovide electrical input signals to the controller, which is discussedbelow in greater detail. It will be understood that other types ofsensors could be used instead of electromechanical limit switches orHall-effect switches, such as optoelectronic sensors, or magneticsensors, or even a metal-sensing proximity switch.

Also viewed on FIG. 25 is a return spring 436, which causes the safetycontact element 418 to be pushed back downward (in this view) once theuser releases the nose of the tool 401 from the working surface. Inaddition, there is a depth of drive adjustment at 438.

As generally indicated on FIG. 26 at a reference numeral 498, the driver490 may be driven toward the exit end by a type of driver actuationdevice other than a gas spring. For example, the driver member 490 couldhave a top circular area 497 that is forced downward (in this view) by amechanical spring 496, which could be a fast-acting coil spring, forexample, thereby also causing driver 490 to move downward (in thisview). Or an alternative driver actuation device could use a differenttype of mechanical force, for example, applied by compressed foam (inthe area at 498). In such alternative embodiments, there would be noneed for a cylinder at all, and instead the spring 496 (or other deviceat 498) would merely need a mechanical guide to keep it moving in acorrect motion.

Further alternative ways to force the driver 490 of FIG. 26 to move in adriving stroke toward the exit end are the use of a fast-acting motor,or the use of a compressed gas valve (releasing compressed air into acylinder against, for example, a piston 458 instead of the circular area497), or perhaps a pressurized liquid valve (releasing pressurizedhydraulic fluid into a cylinder against the piston 458, for example). Ifa piston 458 is used with compressed gas or pressurized liquid, then acylinder (not shown) would also be added to the unit of FIG. 26, insteadof merely using a mechanical guide.

Referring now to FIG. 27, further details of the solenoid are viewed. InFIG. 27, the solenoid 440 has a plunger 442 that will move linearlyeither in or out from the main coil body of the solenoid 440. When thesolenoid is energized, it pulls the plunger 442 in toward the solenoidbody 440, which rotates a solenoid arm 446 (part of the solenoid's“linkage”), which in turn rotates the latch shaft 422 that also rotatesthe latch 420 a small arcuate distance. This causes the latch 420 todisengage from an interfering position with the driver 490. On the otherhand, when the solenoid 440 becomes de-energized, the plunger will bepushed out by the plunger spring 444, which will rotate the solenoid arm446 a short distance, and that in turn rotates the latch shaft 422 andthe latch 420. This will tend to cause the latch to engage the teeth 491along the right-hand side (as seen in FIG. 20) of the driver 490.However, since this is a spring action, the teeth 491 can slide againstthe surface of the latch 420 and move the latch out of the way if theteeth are attempting to move upward along with the driver 490. However,the spring action of the solenoid plunger spring will be strong enoughto push the latch 420 into its engaged position, and any teeth 491attempting to move downward will be caught by the catching surface 424of the latch 420.

This “catching” action of the latch 420 has more than one benefit. Inthe first place, the latch remains in its interfering position as thepiston 458 is lifted to its top or “firing” position. The driver 490cannot be fired until the latch 420 is moved out of the way, asdiscussed above. On the other hand, if there is some type of jam or animproper use of the tool by a user such that the driver 490 does nottotally complete its travel during a firing (driving) stroke, the latch420 will also prevent a misfire from occurring at an inconvenient time.

More specifically, if the driver jams during a driving stroke, and if aperson tries to clear the jam, and if there was no precaution taken toprevent the remainder of the stroke from occurring at that moment, thenpossibly an injury could occur when the driver 490 suddenly becomesreleased from its jammed condition. In other words, a fastener could bedriven during the attempt to clear the jam, and that fastener wouldlikely be directed somewhere that is not the original target surface. Inthe present invention, the latch 420 will have its solenoid 440 becomede-energized once the jam occurs (because solenoid 440 will de-energizeafter a “timeout” interval occurs), and therefore the latch 420 will beengaged and the catching surface 424 will be in a position to interferewith the downward movement of the driver teeth 491. By use of thisconfiguration, the driver could only move a short distance even if thejam was suddenly cleared, because the latch catching surface 424 willliterally “catch” the “next” tooth 491 that unexpectedly comes alongduring a downward travel of the driver 490. This makes the tool muchsafer in situations where a complete driving stroke has not occurred.

The process for controlling the solenoid and the moments when thesolenoid will either be energized or de-energized are discussed below inconnection with the flow chart that begins on FIG. 35.

It will be understood that the latch 120 or 420 could be controlled by adevice other than a solenoid, without departing from the principles ofthe present invention. For example, the solenoid 140 or 440 could bereplaced by motor, or some type of air or hydraulic valve, if desired.Moreover, the latch action could be linear rather than rotational(pivotable), if desired.

With respect to various types of firing (or driving) modes, a “triggerfire” mode is where the user first presses the tool nose against aworking surface, and then depresses the trigger actuator 439. It is thetrigger being depressed that causes the driving stroke to occur in thissituation. With respect to a “bottom fire” mode, the trigger is actuatedfirst, and then the user presses the nose of the tool against a worksurface, and it is the work surface contact that causes the drivingstroke to occur. As discussed above, the user can continue to hold thetrigger down while pressing against and releasing the tool from the worksurface multiple times, and obtain quick multiple firing strokes (ordriving strokes), thereby quickly dispensing multiple fasteners into theworking surface at various locations.

There is also an optional “restrictive firing mode,” in which the noseof the tool must be first placed against a working surface before thetrigger is pulled. If the sequence of events does not unfold in thatmanner, then the driving stroke will not occur at all. This is strictlyan optional mode that is not used by all users, and certainly in not allsituations.

With regard to alternative embodiments of the present invention secondembodiment, an exemplary fastener driving tool can be made with a mainstorage chamber volume of about 11.25 cubic inches and a cylinderdisplacement volume of about 3.75 cubic inches. This would provide avolumetric ratio of the main storage chamber versus the displacementvolume of about 3.0:1. As discussed above, it is desirable for thevolumetric ratio of the main storage chamber's volume to thedisplacement volume to be at least 2.0:1, and it could be much higher ifdesired by the fastener driving tool's designer.

The working pressure in the system could be around 120 PSIG, and shouldprobably be at least 100 PSIG for a quick-firing tool. By the term“working pressure” the inventors are referring to the pressure in thedisplacement volume 457 (and main storage chamber 454) at the time thepiston 458 is at its “ready” position, which is when it is at (orproximal to) its uppermost travel position.

It should be noted that other gases besides air can be used for the mainstorage chamber and the displacement volume, if desired. While air willwork fine in many or most applications, alternative gases could be usedas the “charge gas,” such as carbon dioxide or nitrogen gas. Moreover,the use of nitrogen gas can have other benefits during the manufacturingstage, such as for curing certain adhesives, for example.

In the illustrated second embodiment, there is no fill valve on thefastener driving tool 401 at the storage tank (main storage chamber)454. This is a preferred mode of the present invention, although anoptional fill valve could be provided, if desired by a tool designer.The design of the preferred mode of the present invention is such thatthe charge gas should not significantly leak from the tool, andtherefore a fill valve would not be required.

Another feature of the present invention is that a variable stroke ispossible by causing the rotary-to-linear lifter 400 to be rotated amultiple number of times to create a shorter or longer firing (driving)stroke, if desired. In the illustrated second embodiment, the lifter 400makes a complete rotation two times to lift the piston from itslower-most position to its top-most position. This number of rotationsof the lifter could be increased to three times or four times ifdesired, or even could be decreased to a single turn for a shorterstroke tool, if desired.

Another possible variation is to use a composite sleeve for the internalcylinder wall 451, which would make contact with the seals of the piston458. In addition, the outer pressure vessel wall 456 could also be madeof a composite material, if desired. The use of a carbon fibercomposite, for example, would decrease weight, but would maintain thedesired strength.

Referring now to FIG. 28, some of the details of the piston arrangementare illustrated in cross-section for the second embodiment 401 of thepresent invention. This piston is designated by the reference number458. There are upper and lower seals at 482 and 484, respectively.Between these seals is an annular space 486 that is at least partiallyfilled with lubricating fluid, such as oil. This oil will tend tolubricate the movements of the piston 458 along the inner surface of thecylinder wall 451. Part of the piston mechanism of this embodimentincludes a piston scraper 489.

The seals 482 and 484 are designed to hold the oil 488 within theannular space 186 indefinitely, or at least to lose the oil only at avery slow rate. In a preferred mode of the invention, the seals have a“slick” coating material to provide a long operational life. In theillustrated embodiment, an exemplary material for this coating isXYLAN™, which is a TEFLON™ material that includes molybdenum powder.

The driver element 90 of tool 10 and the driver element 490 of tool 401both retract into their respective working cylinder areas 71 and 453.This is a unique arrangement, in that some of the driver's latchingprotrusions (or “teeth”) 92 and 491 also retract into the workingcylinder areas 71 and 453. This is made possible by the positioning ofthe respective lifters 100 and 400, and by the shapes of the driverelements 90 and 490, and also by the sealing arrangement of the pistons80 and 458, discussed in the previous paragraphs.

It will be understood that the fastener magazine portion 16 of tool 10and the fastener magazine portion 407 of the tool 401 are essentiallyoptional features. In other words, the fastener driving tools 10 and 401could be constructed to act as “single-shot” devices, and no magazinewould be provided for such a tool. Alternatively, the tools 10 and 401could be provided with a standard detachable magazine, but the toolsthemselves could also be constructed to work in a “single-shot mode”such that a single fastener is placed in the tool 10 or 401, near itsfront end or tip (e.g., near 30) and that single fastener is then drivenby tool 10 or 401. In this mode, the magazine 16 or 407 could bedismounted from the tool 10 or 401 during the single-shot procedure;later, the magazine 16 or 407 could be re-mounted to the tool 10 or 401,and the collated fasteners in the magazine could then be driven by thetool, as desired by the user.

Referring now to FIG. 30, an alternative embodiment rotary-to-linearlifter is illustrated, generally designated by the reference numeral460. Lifter 460 has only a single protrusion (or “pin”) at 462, and thelifter 460 rotates about a pivot axis at 461. The outer perimeter shapeof lifter 461 is mainly arcuate at 464, and only comprises a smallsector of a full circle. Yet lifter 460 can achieve the goals of thepresent invention, in that its protrusion 462 will provide adiscontinuous contact surface with the “teeth” of a driver element, suchas the driver 90 or driver 490. Lifter 460, having only a single “pin”would need to rotate more quickly that the other lifters 100 and 400,described above and in the drawings showing the first and secondembodiments of a tool 10 or 401 (assuming that it was attempting to lifta driver having the same size and shape, and “teeth” spacings, as thosepreviously described drivers).

Referring now to FIG. 31, another alternative embodimentrotary-to-linear lifter is illustrated, generally designated by thereference numeral 465. Lifter 465 has two protrusions (or “pins”) at 467and 468, and the lifter 465 rotates about a pivot axis at 466. The outerperimeter shape of lifter 465 has a very irregular geometric shape at469. Yet lifter 465 can achieve the goals of the present invention, inthat its protrusions 467 and 468 will provide a discontinuous contactsurface with the “teeth” of a driver element, such as the driver 90 ordriver 490. Lifter 465, having only two “pins” would need to rotate morequickly that the other lifters 100 and 400, described above and in thedrawings showing the first and second embodiments of a tool 10 or 401(assuming that it was attempting to lift a driver having the same sizeand shape, and “teeth” spacings, as those previously described drivers).

Referring now to FIG. 32, yet another alternative embodimentrotary-to-linear lifter is illustrated, generally designated by thereference numeral 470. Lifter 470 has three protrusions (or “pins”) at472, 473, and 474, and the lifter 470 rotates about a pivot axis at 471.The outer perimeter shape of lifter 471 has a very regular geometricshape at 475, which is that of a circle. Yet lifter 470 can achieve thegoals of the present invention, in that its protrusions 472, 473, and474 will provide a discontinuous contact surface with the “teeth” of adriver element, such as the driver 90 or driver 490. Lifter 470, havingthree “pins” would need to rotate generally at the same speed as theother lifters 100 and 400, described above and in the drawings showingthe first and second embodiments of a tool 10 or 401 (assuming that itwas attempting to lift a driver having the same size and shape, and“teeth” spacings, as those previously described drivers).

Referring now to FIG. 33, still another alternative embodimentrotary-to-linear lifter is illustrated, generally designated by thereference numeral 480. Lifter 480 has two protrusions (or “pins”) at 482and 483, and the lifter 480 rotates about a pivot axis at 481. The outerperimeter shape of lifter 481 has a very regular geometric shape at 484,which is that of a square. Yet lifter 480 can achieve the goals of thepresent invention, in that its protrusions 482 and 483 will provide adiscontinuous contact surface with the “teeth” of a driver element, suchas the driver 90 or driver 490. Lifter 480, having only two “pins” wouldneed to rotate more quickly that the other lifters 100 and 400,described above and in the drawings showing the first and secondembodiments of a tool 10 or 401 (assuming that it was attempting to lifta driver having the same size and shape, and “teeth” spacings, as thosepreviously described drivers).

Referring now to FIG. 35, a logic flow chart is provided to show some ofthe important steps used by a system controller for the fastener drivingtool 401 of the second illustrated embodiment for the present invention.Starting at an initializing step 500, a step 502 loads registers withpredetermined values, and a step 504 loads special function registerswith predetermined values. A step 506 now “checks” the RAM (RandomAccess Memory) to be sure it is functioning properly, and then a step508 clears the RAM. A step 510 now loads unused RAM with predeterminedvalues, based on the software coding for the system controller(typically in firmware or hard-coded).

A step 512 now determines the stability of the system electrical powersupply. Then a step 514 causes an electrical output to blink one or moreLEDs (light-emitting diodes) 443 on tool 510, so the user is made awarethat the tool 510 has entered its “startup” mode of operation. Step 514also initializes the interrupts that will be used for the controller,and the controller is now ready to enter into an operational routine.

A decision step 516 now determines if the safety has been actuated(i.e., whether the safety contact element 418 has been pressed against asolid object to an extent that actuates the sensor, e.g., limit switch432). Step 516 also determines if the trigger 439 has been pulled. Ifthe answer is YES for either of these questions, then the logic flow isdirected to a step 520. If the answer is NO for both of these questions,then the logic flow is directed to another decision step 518.

Step 518 determines whether or not the LEDs 443 have flashed apredetermined maximum number of times. If the answer is YES, then thelogic flow is directed to step 520. If the answer is NO, then the logicflow loops back to step 514.

At a step 520, the control logic enters a “BEGIN” routine. A decisionstep 540 now determines whether or not the current operating mode is the“RESTRICTIVE” mode. This determination involves inspecting the currentstate of the selector switch 441 which, as noted above, has threepositions: “Off”, “Mode A”, or “Mode B”. This three-position switch 441is part of an exemplary arrangement of the second embodiment of thefastener driving tool 401, and in this description of the second toolembodiment, Mode A and Mode B are also referred to as a “RestrictiveMode,” and a “Contact Actuation Mode.”

If the current operating mode is not the RESTRICTIVE mode, then thelogic flow is directed to a decision step 522. On the other hand, if thecurrent mode is the RESTRICTIVE mode, then the logic flow is directed toa step 542 in which the tool enters a “restrictive fire” routine. Thelogic flow is directed now to a decision step 544 that determines if thetrigger has been pulled. If the answer is NO, then the logic flow isdirected to a decision step 541. On the other hand, if the trigger hasbeen pulled, then the logic flow is directed to a step 546 that willfurther direct the logic flow to the “STOP 1” function (or routine) at astep 680 on FIG. 37. It should be noted that, in the “restrictive fire”mode of operation, the trigger cannot be pulled first; instead the noseof the fastener driving tool must be pushed against the solid surfacebefore the trigger is pulled. In other words, this particular “firingmode” is a predetermined sequential mode of operation (and the term“restrictive fire mode” is also referred to herein as the “sequentialmode”).

If the logic flow at decision step 544 resulted in a NO result, thelogic flow at decision step 541 determines whether or not the safety hasbeen actuated. If the answer is NO, then the logic flow is directed backto the “restrictive fire” routine, just before step 544. However, if theanswer is YES, the logic flow is directed to a step 543, in which thecontroller turns on the “work light,” which is a small electric lamp(e.g., an LED) that illuminates the workpiece where the fastener is tobe driven.

A decision step 545 now determines whether or not a “sequential modetimeout” has occurred, and if the answer is YES, the logic flow isdirected to a step 547 that directs the logic flow to the “STOP 1”function at step 680 on FIG. 37. This temporarily stops the tool fromoperating. On the other hand, if the timeout has not yet occurred, thelogic flow is directed to a decision step 548 that determines whetherthe trigger has been pulled. If the answer is NO, the logic flow isdirected back to the decision step 544. On the other hand, if the answeris YES, the logic flow is directed to a step 549 that causes the tool toenter the “DRIVE” mode of operation at step 560 on FIG. 36.

If the answer at step 540 was NO, the decision step 522 now determineswhether or not the trigger has been pulled. If the answer is YES, thelogic flow is directed to a step 530 in which the logic flow enters a“TRIGGER” routine. A step 531 turns on a “work light,” which is the samelamp/LED that was discussed above in reference to step 543.

A decision step 532 now determines whether or not a predetermined“trigger timeout” has occurred, and if the answer is YES, a step 534directs the logic flow to a “STOP 1” routine, that is illustrated onFIG. 37 at a step 680. What this actually means is that a user pulledthe trigger, but then did not actually use the tool against a solidsurface, and rather than having the tool ready and primed to fire afastener at any moment for an indefinite period of time, a predeterminedamount of time will pass (i.e., the “timeout” interval), and once thathas occurred, the system will be basically deactivated in the STOP 1mode. This is not a permanent stoppage of the functioning of the tool,but is only temporary. Note that the “timeouts” are interrupt driven, inan exemplary embodiment of the present invention.

If the timeout has not occurred at decision step 532, then a decisionstep 536 determines if the safety has been actuated. If the answer isNO, then the logic flow is directed back to the BEGIN routine 520. Onthe other hand, if the safety has been actuated at step 536, then thelogic flow is directed to a step 538 that will send the logic flow to a“DRIVE” routine, which is on FIG. 36 at a step 560. This will bediscussed below in greater detail.

If, at step 522, the trigger was not yet pulled, then the logic flow isdirected to the decision step 524. When the logic flow reaches decisionstep 524, the logic now determines whether or not the safety has beenactuated. This step determines whether or not the safety contact element418 has been pressed against a solid object to an extent that actuatesthe sensor (e.g., limit switch 432), which means that the tool is nowpressed against a surface where the user intends to place a fastener. Ifthe answer is NO, the logic flow is directed back to the mode switchquery at decision step 540. However, if the answer is YES, the logicflow is directed to a step 550 in which the controller enters a “SAFETY”routine.

Once at the SAFETY routine at step 550, a step 551 turns on the “worklight,” which is the same lamp/LED that was discussed above in referenceto step 531. A decision step 552 now determines whether or not a “safetytimeout” has occurred, and if the answer is YES, the logic flow isdirected to a step 554 that directs the logic flow to the “STOP 1”function at step 680 on FIG. 37. This temporarily stops the tool fromoperating. On the other hand, if the timeout has not yet occurred, thelogic flow is directed to a decision step 556 that determines whetherthe trigger has been pulled. If the answer is NO, the logic flow isdirected back to the decision step 524. On the other hand, if the answeris YES, the logic flow is directed to a step 558 that causes the tool toenter the “DRIVE” mode of operation at step 560 on FIG. 36.

As can be seen by reviewing the flow chart of FIG. 35, unless the tool401 is in the restrictive fire mode (at step 542), the tool can beactuated with either one of the two important triggering steps occurringfirst: i.e., the trigger could be pulled before the safety is actuated,or vice versa.

Referring now to FIG. 36, the logic flow from FIG. 35 is directed to the“DRIVE” routine 560 from two other steps on FIG. 35: these are step 538and step 558. Once at the DRIVE routine 560, a switch debounce step 562is executed to determine whether or not one or both of the triggeringelements was somehow only actuated intermittently. If so, the systemdesigners have determined that the tool should not operate until it ismore certain that the input switches have actually been actuated. To dothis, the logic flow is directed to a decision step 564 to determine ifthe safety is still actuated. If the answer is NO, then the logic flowis directed to a step 566 that sends the logic flow back to the SAFETYroutine at step 550. On the other hand, if the safety still is actuatedat step 564, then the logic flow is directed to a decision step 570 todetermine if the trigger is still being pulled. If the answer is NO,then the logic flow is directed to a step 572 that sends the logic flowback to the TRIGGER routine at step 530.

On the other hand, if decision steps 564 and 570 are both answeredaffirmatively, then a step 580 clears the operational timers, and thelogic flow is then directed to a decision step 582 that determines ifthe software code flow is within certain parameters. This is afault-checking mode of the software itself, and if the system does notdetermine a satisfactory result, then the logic flow is directed to astep 584 that sends the logic flow to a “STOP” routine at a step 670 onFIG. 37. This will ultimately turn the tool off and require a safetyinspection of the tool, or at least have the tool reset. However, thetool does not need to be completely disabled, and after the safetyinspection and tool reset procedure, the tool will be ready to use againwithout being sent to a service center. In an exemplary mode of theinvention, the code flow check step determines if a correct numberresides in a register or memory location; this number is the result ofbeing incremented at predetermined executable steps of the software forthe system controller.

If the software code flow check is within acceptable parameters atdecision step 582, then the logic flow is directed to a step 590 thatturns on the motor, and then a step 592 that turns on the solenoid. Astep 594 now starts the solenoid timer and a step 596 now starts themotor run timer. As will be discussed below, these timers will beperiodically checked by the system controller to make sure that certainthings have occurred while the solenoid is on and while the motor isrunning Otherwise, after a predetermined maximum amount of time, themotor will be turned off and the solenoid will be turned off due tothese timers actually timing out, which should not occur if the tool isbeing used in a normal operation, and if the tool is functioningnormally.

In addition to the solenoid and motor run timers discussed above, a“dwell timer” is used to allow the tool to begin its normal operationbefore any further conditions are checked. This is accomplished by adecision step 598 on FIG. 36, which causes the logic flow to essentiallywait a short amount of time before continuing to the next logic steps.

Once the dwell timer has finished at step 598, the logic flow isdirected to a decision step 600 that determines if the solenoid “ontime” has been exceeded. If the answer is YES, the logic flow isdirected to a step 602 that turns off the solenoid. This situation doesnot necessarily mean the tool is being misused or is not functioningproperly, and therefore the logic flow does not travel to a “stop step”from the step 602. Instead, the logic flow is directed to a decisionstep 604, discussed below.

If the solenoid on time has not been exceeded, then the logic flow alsois directed to the decision step 604, which determines if the cam limitswitch has received a first signal. This is the Hall effect sensor 430that detects the presence or absence of the magnet 414 of the lifter. Ifthe tool of the illustrated embodiment is being used, the lifter 410will make two complete rotations when lifting the driver and piston fromtheir bottom-most positions to their top-most positions. Therefore, thecam limit switch 430 will receive two different signals during thislift. Step 604 determines if the first signal has occurred. If not, thena decision step 610 determines whether the motor timeout has occurred.If the answer is NO, then the logic flow is directed back to decisionstep 600. On the other hand, if the motor run timer has indeed timedout, then the logic flow is directed to a step 612 that sends the logicflow to a “STOP” routine at step 670. This would likely indicate thatthere is a problem with the tool, or a problem with the way the user isattempting to operate the tool.

Referring back to decision step 604, if the first signal from the camhas occurred, then the logic flow is directed to a step 606 that turnsoff the solenoid. This will allow the latch 420 to engage the teeth 491of the driver 490, in case there has been some type of jam, or othertype of unusual operation while the driver and piston are being lifted.It also allows the latch 420 eventually to properly engage thebottom-most tooth 426 of the driver, which is the normal operation oncethe driver and piston have been raised to their top-most (or firing)position.

The logic flow is now directed to a decision step 620 that determineswhether a second signal has been received from the cam limit switch. Ifthe answer is NO, then the logic flow is directed to a decision step 622that determines whether or not the motor run timer has timed out. If theanswer is NO, then the logic flow is directed back to decision step 620.On the other hand, if the motor timer has timed out, the logic flow isdirected to a step 624 that directs the logic flow to the “STOP” routineat 670, and indicates that there is some type of problem.

Once decision step 620 determines that the second signal from the camhas been received, then the logic flow is directed to a step 630 thatturns off the motor, then to a step 632 that starts a “reset” timeoutreferred to as “all switches on.” In this mode, it is either assumedthat both the actuation (input) devices are still actuated, or at leastthat the controller needs to make an examination of those input devicesto see what the proper status of the tool should be. Accordingly, thelogic flow is first directed to a decision step 634, which determineswhether the operator mode selector switch 441 is set to the RestrictiveMode, and if not, the logic flow is directed to a decision step 640(discussed below).

If the answer is YES at step 634, the logic flow is directed to adecision step 635 that determines whether or not the reset timeout hasoccurred. If the answer is YES, then the logic flow is directed to astep 636, and the tool is then enters the STOP1 routine at step 680 onFIG. 37. If the answer was NO at step 635, a decision step 637determines whether or not the safety is still actuated (or “pulled”). Ifthe answer is YES, then the logic flow is directed back to step 635; ifthe answer is NO, the logic flow is directed to a decision step 638which determines whether or not the trigger is still being pulled. Ifthe answer is YES, then the logic flow is directed back to step 635; ifthe answer is NO, the logic flow is directed to a step 639, and the toolthen enters the BEGIN routine at step 520 on FIG. 35.

Back at step 634, if the current selector switch mode was notRestrictive, then the logic flow is directed to a decision step 640 thatdetermines if the safety is still actuated. If the answer is NO, thenthe logic flow is directed to a step 642 that then sends the logic flowto the “BEGIN” routine at step 520 on FIG. 35. On the other hand if thesafety is still actuated, the logic flow is directed to a decision step650 that determines if the trigger is still pulled. If the answer is NO,then the logic flow is directed to a step 652 that also directs thelogic flow to the “BEGIN” step at 520 on FIG. 35. Finally, if thetrigger is still being pulled, then a decision step 660 determineswhether or not a “reset” timeout has occurred, and if the answer is YES,the logic flow is directed to a step 662 that sends the logic flow tothe “STOP 1” routine at step 680 on FIG. 37. If the reset timeout hasnot yet occurred at step 660, then the logic flow is directed back tothe decision step 640 and the inspection of all of the switches willagain be performed.

The logic flow is continued on FIG. 37, in which there are two differenttypes of stop routines. The routine called “STOP” at step 670 will firstturn off the motor at a step 672, turn off the solenoid at a step 674,and turn off the work light at a step 676. The STOP routine will thenclear the timers at a step 678. The logic flow then becomes a “DO-Loop,”and continues back to the STOP routine at step 670. This is a faultmode, and the tool must be inspected. As a minimum, it needs to be resetto terminate the DO-Loop processing of the software, which means thatthe battery must be disconnected from the tool. If the user has beenusing the tool properly, this may be an indication that there is someoperational problem with the tool itself, or that a fastener perhaps hasjammed somewhere in the tool and the operator did not notice that fact.

The other type of STOP routine is the “STOP 1” routine at step 680. Oncethat occurs, a step 682 turns off the motor, turn off the solenoid at astep 684, and turn off the work light at a step 686. The STOP 1 routinewill then clear the timers at a step 688, and a decision step 690determines whether or not the trigger is still pulled. If the answer isYES, then the logic flow is directed back to the STOP 1 routine at step680. If the trigger is not pulled at step 690, the logic flow is thendirected to a decision step 692 that determines if the safety is stillactuated. If YES, the logic flow is directed back to the STOP 1 routineat step 680. However, if the safety is not actuated, the logic flow isdirected to a step 698 that sends the logic flow to the “BEGIN” routineat step 520 on FIG. 35. At this point, the tool has been successfullyused, and is ready for the next firing (driving) actuation.

Referring now to FIG. 38, an alternative embodiment of arotary-to-linear lifter mechanism is illustrated, and is generallydesignated by the reference numeral 800. In FIG. 38, the opposite side(compared to certain earlier views of lifter 100, such as FIGS. 3-5) oflifter 800 is seen. Three extensions or “pins” 804, 806, and 808 aredirectly seen in this view, and this is the “working side” of thosethree pins, which are designed to make contact with the teeth 892 of adriver 890 (see FIG. 39). FIG. 38 shows the positional relationship ofthese three pins with respect to the lifter mechanism 800 and the centerposition for its lifter drive shaft 802, in an exemplary alternativeembodiment. In addition, FIG. 38 shows the semi-circular outer shape ofa first part of the perimeter of the lifter at 816, and the moreelliptical outer shape of a second part of the perimeter of the lifterat 810, similar to the perimeter portions 110 and 116, discussed above.The outer shape of the perimeter portions (at 810 and 816) define anouter perimeter of a surface or “face” 812 from which these pins 804,806, and 808 protrude.

The lifter pin 804 is also referred to as the “first pin,” while the pin806 is also referred to as the “second pin,” and the pin 808 is alsoreferred to as the “third pin,” mainly because these pins 804, 806, and808 engage the driver's teeth 892 in that order, as the lifter 800rotates during a lifting event of the driver 890. The third pin 808 isalso known as the “last pin,” because when the lifter 800 rotates pastthe point where “last pin” 808 makes contact with one of the driverteeth 892, then the driver 890 can move quickly downward (in theorientation of most of the views herein) to create a driving stroke toforce a fastener into a target workpiece.

The geometry of the outer surface of the last lifter pin 808 isimportant: as illustrated on FIG. 38, pin 808 exhibits a substantiallycircular shape at 842 for most of its outer perimeter (as seen in thisview). However, this circular shape is cut off at two outer corners, 844and 846. A substantially flat surface (having a linear appearance inthis view) at 840 runs between those two corners. This geometry reducesthe side forces that otherwise would be imparted to the edge of thedriver 890, which will be discussed in detail below, with respect toFIGS. 43 and 44.

It will be understood that the lifter pins 804, 806, and 808 are alsosometimes referred to herein as spaced-apart “extensions” that originatein the face 812 of the lifter mechanism 800. The last pin 808 is alsosometimes referred herein as the “final one” of the spaced-apartplurality of extensions, and is said to have a geometric shapecomprising: an arcuate shape for a portion of its outer perimeter, andat least two outer corners with a substantially linear facetherebetween. The arcuate shape is at 842, the two outer corners are at844 and 846, and the substantially linear face is at 840.

As can be seen in FIG. 38, there is an abrupt angular change indirection along the outer perimeter of lifter pin 808, at a locationbetween first and second portions of said outer perimeter, in which thefirst portion is the arcuate shape 842, and the second portion is therelatively flat (or planar) shape at 840. The second portion between theouter corners 844 and 846 is also sometimes referred to herein as a“cut-off face” or a “cut-off surface” of lifter pin 808.

Referring now to FIG. 39, the lifter 800 has rotated to a position wherethe “first pin” 804 is making contact with one of the driver teeth, andtherefore, is able to raise the driver 890 upward (in this view) whenthe lifter 800 rotates in the correct direction, which would be thecounterclockwise direction in this view. Most of the driver teeth havethe same shape, i.e., those teeth designated by the reference numeral892. However, the “top tooth” at 894 is elongated; this also is the“first tooth” that is engaged by the lifter pins at the beginning of alift cycle. In FIG. 39, the pin 804 is making contact with the tooth 894along a surface 850, which essentially is the bottom surface (in thisview) of the tooth 894.

The opposite side of the driver 890 also exhibits an alternative shape,at reference numeral 896. This alternative shape is better seen in theperspective view of FIG. 42, and will be discussed below, in referenceto that view. The driver 890 is mechanically connected to a piston 880,as seen in FIG. 39, which performs the same functions as the piston 80,described above and illustrated in FIG. 2, and in other views. Thisalternative embodiment includes a guide body 836, which is similar tothe guide body 36, described above and illustrated in FIG. 3, and inother views.

Referring now to FIG. 40, the lifter 800 has rotated to a position wherethe “second pin” 806 is making contact with one of the driver teeth 892;moreover, the “third pin” 808 is about to make contact with a differentone of the driver teeth 892. This assures a smooth transition when thesecond pin 806 releases from its contact with its particular drivertooth 892—as the second pin 806 releases from contact at a point 852,the third pin 808 quickly begins to make contact at a point 854, andthis keeps the upward (in this view) movement of the driver 890 goingalong smoothly. More accurately, the contact “point” 852 is essentiallythe bottom surface of one of the driver teeth 892, and the contact“point” 854 is essentially the bottom surface of the “next” one of thedriver teeth 892. This is easily discerned by viewing FIG. 40.

Referring now to FIG. 41, the lifter 800 has rotated to a position wherethe “third pin” 808 is about to release its contact with one of thedriver teeth 892, at a point 856. As the lifter 800 continues to rotatein the counterclockwise direction (in this view), the corner 846 of thepin 808 will suddenly go by the point in space where it can touch thedriver tooth 892. As soon as that occurs, the driver 890 will be quicklyforced downward (in this view) by the gas pressure stored in thedisplacement volume of the working cylinder 71 of the tool. Just beforethat occurs, the mechanical forces on the lifter pin 808 and on thedriver 890 will be at a maximum value.

In the earlier embodiments, the “third pin” was entirely circular (asseen in FIG. 8, for example, for pin 108). The working forces, justbefore the pin 108 released from contact with one of the driver teeth92, are illustrated in a vector force diagram, seen on FIG. 43. Thisdiagram of FIG. 43 illustrates a “pin contact lift force diagram,” andshows the positions of a driver 90, a “third pin” 108, a lifter 100, andthe lifter's rotational shaft 102, thereby indicating its center (oraxis) of rotation “C1”. The arrow “GP1” indicates the direction of theforce produced by gas pressure in the working cylinder. The arcuatearrow “R1” indicates the direction of rotation of the lifter 100. Theline “L1” indicates a hypothetical line connecting the lifter's center(“C1”) and the pin's center.

The bottom portion of the driver's tooth 92 is indicated at referencenumeral 93, and this is the location where the pin 108 physicallycontacts the driver 90. The triangle overlaying the pin 108 indicatesthe lift force developed by the lifter 100 at the interface between thelift pin 108 and the driver tooth 92. This force triangle has threecomponents: “F1”, the total lift force; “V1”, the vertical component ofthe lift force F1—note that this component force V1 is equal to the gaspressure force; and “H1”, the horizontal component of the lift force F1.

Note that, as the pin-driver tooth contact moves beyond the hypotheticalline L1, due to lifter rotation, the relative size of the horizontal andvertical lift forces (H1 and V1) switch in magnitude. This change inorientation causes a significant change in normal loading between thepin 108 and the driver 90. This normal loading causes a proportionalincrease in friction between the driver and the lifter pin. For a fullround pin, as in the embodiment of FIG. 3 and FIG. 12, the horizontalforce component H1 can become extremely large as the lifter rotationcontinues farther than shown in FIG. 43.

In the alternative embodiment illustrated in FIGS. 38-42, the workingforces, just before the pin 808 releases from contact with one of thedriver teeth 892, are illustrated in a vector force diagram, seen onFIG. 44. This diagram of FIG. 44 illustrates a “pin contact lift forcediagram,” and shows the positions of a driver 490, a “third pin” 808, alifter 800, and the lifter's rotational shaft 802, thereby indicatingits center (or axis) of rotation “C2”. The arrow “GP2” indicates thedirection of the force produced by gas pressure in the working cylinder.The arcuate arrow “R2” indicates the direction of rotation of the lifter800. The line “L2” indicates a hypothetical line connecting the lifter'scenter (“C2”) and the pin's center.

The bottom portion of the driver's tooth 892 is indicated at referencenumeral 893, and this is the location where the pin 808 physicallycontacts the driver 890. The triangle overlaying the pin 808 indicatesthe lift force developed by the lifter 800 at the interface between thelift pin 808 and the driver tooth 892. This force triangle has threecomponents: “F2”, the total lift force; “V2”, the vertical component ofthe lift force F2—note that this component force V2 is (again) equal tothe gas pressure force; and “H2”, the horizontal component of the liftforce F2.

The two force diagrams of FIGS. 43 and 44 are not to scale; if theywere, then it would be quite clear that the horizontal force H2 is muchless than the horizontal force H1, keeping in mind that the verticalforces V1 and V2 are equal to one another. (V1 and V2 are equal to thegas pressure, which is the same in both embodiments for a given powerstroke.) The location of the corner 846 is started close to the pointwhere the hypothetical line L2 crosses the pin face. This change indesign guarantees a limited horizontal component of force, and any lossof lift height is minimal. Moreover, in this embodiment, the lifter pin808 is “cut” at a large enough angle to ensure that the driver 890 willclear the pin 808 as it releases from the driver tooth 892. This cut-offangle is designated by the letter “A” on FIG. 38.

It should be noted that, on FIG. 44, the magnitude of the horizontalforce H2 is less than that for the vertical force V2, which is theopposite case compared to the force diagram of FIG. 43, where H1 wasgreater in magnitude than V1. This shows a major advantage of thealternative embodiment described herein, starting on FIG. 38. Therotational position of the corner 846, and its cut-off angle A,determine the effectiveness of the side-loading force reductioncharacteristics. So long as the internal parts have not been damaged andthe friction of the lifter subassembly system has not been compromiseddue to dirt or debris entering into the mechanism, the lift forceside-load component (e.g., H2) should not equal or exceed the lift forcein the perpendicular direction (e.g., the V2 force component).

Referring now to FIG. 42, the alternative embodiment for the driver 890is more clearly illustrated in this perspective view. Along one edge ofthe driver are a series of teeth 892, and also a larger “first tooth” at894; these driver teeth were discussed in some detail above, inconnection with FIGS. 39-41. As can be seen in FIG. 42, the lifter pins806 and 808 are sized and shaped to fit in the openings between thesemultiple teeth 892, as the lifter mechanism 800 rotates.

Along the opposite edge of the driver 890 are a series of openings 898that are formed in a raised wall 897 that extends at a substantiallyperpendicular angle from that opposite edge; this forms a “slotted rib”structure, in appearance. The earlier embodiments (such as driver 90,illustrated in FIGS. 3-8) included a plurality of raised teeth 92 thatwere virtually identical to the teeth that were formed along theopposite edge—i.e., the edge that engaged with the rotatable lifter 100.In those earlier embodiments, there were spaces between the top surfacesof the multiple teeth. However, in the alternative embodiment of FIG.42, there is a single continuous top surface or “face” at 896, whichruns along the entire length of the portion of the driver 890 thatcontains the series of openings 898. The raised wall presents asubstantially planar surface 897 for the latch member to work against,such that the latch member may slide along the raised wall, except atlocations where one of the spaced-apart openings 898 appears in theraised wall.

The alternative embodiment of FIG. 42 also includes a different designfor the latch mechanism, generally designated by the reference numeral820. Latch mechanism 820 works in much the same manner as the latch 120of the earlier embodiment illustrated in FIG. 6, but with somedifferences. In FIG. 6, the latch 120 included a pivotable extensionthat included a “catching surface” at 124, which exhibited an angularouter shape that included an internal corner. This shape was designed toreceive one of the driver teeth 92, and thereby prevent the driver 90from moving downward any farther, once the latch 90 had been engagedwith the driver's teeth. The mechanical loading on the latch's catchingsurface 124 was quite large, since the gas pressure of the tool wasalways present, and particularly if the driver had been lifted almostall the way back toward its starting position. This situation, ifoccurring often due to misuse of the tool, could lead to breakage of thelatch catching surface, at or near one its pointed extensions away fromthe internal corner.

In the alternative embodiment of FIG. 42, the angled catching surfacehas been replaced with a substantial solid surface that has no internalcorners with pointed protrusions that could become broken, due torepeated tool misuse. Instead, the alternative latch design 820 has asingle large extension at 822 that is physically large in size, and ithas a single substantially linear catching surface at 824. The extension822 is sized and shaped to fit within one of the openings 898 in theside wall 897 of the driver 890. The latch 820 is spring-loaded, so ittends to be thrust into these openings 898 as the driver 890 is liftedtoward its starting position; however, the latch still has a “slidingsurface” that allows the driver 890 to slide by without being “caught”by the latch extension 822.

When the driver 890 is forced downward (in the orientation of FIG. 42)by gas pressure, the latch 820 is supposed to be physically out of theway, so that it will not interfere with the movement of the driverduring a driving stroke. However, if an abnormal (or “fault”) conditionoccurs during operation of the tool, then the latch 820 is allowed torotate (or pivot) and force its extension 822 toward the driver 890; inthat circumstance, the relatively solid catching surface 824 will fitinto the “next” opening 898 of the driver, and thereby intercept thedriver 890 to suddenly stop its downward movement. The large, andrelatively smooth, catching surface 824 is capable of multiple suchevents without damage, either to itself, or to the openings 898 of thedriver 890. The more sturdy construction of the alternative embodimentdriver 890, along this smooth face 896, aids in preventing damage toitself. It will be understood that other physical arrangements for thelatch mechanism could be used to achieve a desired effect, such as toprevent or reduce the chance of damage to the parts.

The latch mechanism 820, as well as the earlier-described latches inthis disclosure (e.g., latch 120, latch 420), typically have beendescribed as being biased by a mechanical means, such as a mechanicalspring. However, it will be understood that the biasing mechanism couldbe based on a different principle of operation, such as a magnetic,hydraulic, or pneumatic mechanism, without departing from the principlesof the invention. The important feature is that the latch ispositionally biased in some way, so that it tends to be moved into ainterfering position with respect to the driver 890. This positionalbiasing could be in a rotational direction (e.g., a pivoting action) orin a linear direction.

Referring now to FIG. 45, another alternative embodiment of arotary-to-linear lifter mechanism is illustrated, and is generallydesignated by the reference numeral 900. In FIG. 45, the opposite sideof lifter 800 is seen, similar to FIG. 38. Three extensions or “pins”904, 906, and 908 are directly seen in this view, and this is the“working side” of those three pins, which are designed to make contactwith the teeth 892 of a driver 890 (see FIG. 39). FIG. 45 shows thepositional relationship of these three pins with respect to the liftermechanism 900 and the center position for its lifter drive shaft 802, inan exemplary alternative embodiment. In addition, FIG. 45 shows thesemi-circular outer shape of a first part of the perimeter of the lifterat 916, and the more elliptical outer shape of a second part of theperimeter of the lifter at 910, similar to the perimeter portions 110and 116, discussed above. The outer shape of the perimeter portions (at910 and 916) define an outer perimeter of a surface or “face” 912 fromwhich these pins 904, 906, and 908 protrude.

The lifter pin 904 is also referred to as the “first pin,” while the pin906 is also referred to as the “second pin,” and the pin 908 is alsoreferred to as the “third pin,” mainly because these pins 904, 906, and908 engage the driver's teeth 892 in that order, as the lifter 900rotates during a lifting event of the driver 890. The third pin 908 isalso known as the “last pin,” because when the lifter 900 rotates pastthe point where “last pin” 908 makes contact with one of the driverteeth 892, then the driver 890 can move quickly downward (in theorientation of most of the views herein) to create a driving stroke toforce a fastener into a target workpiece.

The geometry (shape) of the outer surface of the last lifter pin 908 isimportant: as illustrated on FIG. 45, pin 908 exhibits a substantiallycircular shape at 942 for most of its outer perimeter (as seen in thisview). However, this circular shape is cut off at two outer corners, 944and 946. A “cut-off face” surface (having a curved appearance in thisview) at 940 runs between those two corners. This geometry also reducesthe side forces that otherwise would be imparted to the edge of thedriver 890, which were discussed above in detail, with respect to FIGS.43 and 44.

It will be understood that the lifter pins 904, 906, and 908 are alsosometimes referred to herein as spaced-apart “extensions” that originatein the face 912 of the lifter mechanism 900. The last pin 908 is alsosometimes referred herein as the “final one” of the spaced-apartplurality of extensions, and is said to have a geometric shapecomprising: an arcuate shape for a portion of its outer perimeter, andat least two outer corners with a cut-off face therebetween. The arcuateshape is at 942, the two outer corners are at 944 and 946, and thecut-off face is at 940.

As can be seen in FIG. 45, there is an abrupt angular change indirection along the outer perimeter of lifter pin 908, at a location(e.g., corner 946) between first and second portions of said outerperimeter. The first portion is the arcuate shape 942, and the secondportion is the face at 940 that rather abruptly changes direction fromthe arcuate shape (while moving along the perimeter of the pin 908). Thesecond portion between the outer corners 944 and 946 is also sometimesreferred to herein as a “cut-off face” or a “cut-off surface” of lifterpin 908.

As can be seen by viewing both FIGS. 38 and 45, the cut-off face for the“third” lifter pin can have more than one shape, while performing thetask of reducing side forces. The cut-off corner (at 846 or 946) needsto be positioned correctly, and the angles A or B must be such that thepin will clear the driver 890 during its power stroke to drive afastener. The rotational position of the corner 946, and its cut-offangle B, determine the effectiveness of the side-loading force reductioncharacteristics.

In the above detailed description, there are a number of varioustimeouts that may occur during the operation of the tools builtaccording to the present invention. As of the writing of this patentapplication, all of the timeout intervals are set for three (3) seconds.However, each of the timeouts is designed so as to be independentlysettable by the system designer, in case it becomes desirable to alterone or more of the individual timeout intervals (i.e., to a time valueother than three seconds). Normally this would be done in software code(stored in the memory circuit), used to instruct the processing circuitin its operations, although hardware timers could instead be used.

It will also be understood that the logical operations described inrelation to the flow charts of FIGS. 13-15 and FIGS. 35-37 can beimplemented using sequential logic, such as by using microprocessortechnology, or using a logic state machine, or perhaps by discretelogic; it even could be implemented using parallel processors. Onepreferred embodiment may use a microprocessor or microcontroller toexecute software instructions that are stored in memory cells within anASIC. In fact, the entire microprocessor or microcontroller, along withRAM and executable ROM, may be contained within a single ASIC, in onemode of the present invention. Of course, other types of circuitry couldbe used to implement these logical operations depicted in the drawingswithout departing from the principles of the present invention.

It will be further understood that the precise logical operationsdepicted in the flow charts of FIGS. 13-15 and FIGS. 35-37, anddiscussed above, could be somewhat modified to perform similar, althoughnot exact, functions without departing from the principles of thepresent invention. The exact nature of some of the decision steps andother commands in these flow charts are directed toward specific futuremodels of fastener driver tools (those involving Senco Products tools,for example) and certainly similar, but somewhat different, steps wouldbe taken for use with other models or brands of fastener driving toolsin many instances, with the overall inventive results being the same.

Other aspects of the present invention may have been present in earlierfastener driving tools sold by the Assignee, Senco Products, Inc.,including information disclosed in previous U.S. patents and publishedapplications. Examples of such publications are patent numbers U.S. Pat.No. 6,431,425; U.S. Pat. No. 5,927,585; U.S. Pat. No. 5,918,788; U.S.Pat. No. 5,732,870; U.S. Pat. No. 4,986,164; and U.S. Pat. No.4,679,719.

All documents cited in the Background of the Invention and in theDetailed Description of the Invention are, in relevant part,incorporated herein by reference; the citation of any document is not tobe construed as an admission that it is prior art with respect to thepresent invention.

The foregoing description of a preferred embodiment of the invention hasbeen presented for purposes of illustration and description. It is notintended to be exhaustive or to limit the invention to the precise formdisclosed. Any examples described or illustrated herein are intended asnon-limiting examples, and many modifications or variations of theexamples, or of the preferred embodiment(s), are possible in light ofthe above teachings, without departing from the spirit and scope of thepresent invention. The embodiment(s) was chosen and described in orderto illustrate the principles of the invention and its practicalapplication to thereby enable one of ordinary skill in the art toutilize the invention in various embodiments and with variousmodifications as are suited to particular uses contemplated. It isintended to cover in the appended claims all such changes andmodifications that are within the scope of this invention.

While this invention has been described with respect to embodiments ofthe invention, the present invention may be further modified within thespirit and scope of this disclosure. This application is thereforeintended to cover any variations, uses, or adaptations of the inventionusing its general principles. Further, this application is intended tocover such departures from the present disclosure as come within knownor customary practice in the art to which this invention pertains andwhich fall within the limits of the appended claims.

1. A driving mechanism for use in a fastener driving tool, said driving mechanism comprising: (a) a guide body that has a receiving end, an exit end, and a passageway therebetween, said guide body being configured to receive a fastener that is to be driven from said exit end; (b) a movable driver actuation device; (c) an elongated driver member that is in mechanical communication with said movable driver actuation device at a first end of said driver member, said driver member having a second, opposite end that is sized and shaped to push a fastener from said exit end of the guide body, said driver member having a direction of movement between a driven position and a ready position, said driver member having a longitudinal edge, said driver member having a plurality of spaced-apart protrusions along said longitudinal edge; and (d) a lifter member that exhibits a contoured contact surface that, at predetermined locations along said contoured contact surface, makes contact with said plurality of spaced-apart protrusions of said driver member such that, as said lifter member is moved in a first direction, said lifter member causes said driver member to be moved from its driven position toward its ready position, said contoured contact surface comprising a plurality of spaced-apart extensions, a final one of said spaced-apart plurality of extensions having a shape comprising: an arcuate shape for a portion of its outer perimeter, and at least two outer corners with a substantially linear face therebetween; wherein said shape for said final one of the plurality of extensions reduces side-loading forces between said lifter member and said elongated driver member.
 2. The driving mechanism of claim 1, wherein as said lifter member rotates in said first direction to move said driver member toward said ready position, when said final one of said spaced-apart extensions reaches a position where said driver member is ready to perform a driving stroke, then one of said at least two outer corners of said final one of said spaced-apart plurality of extensions releases from contact with said driver member to allow said driver member to move toward its driven position, before a lift force side-load magnitude increases to a value equal to a lift force magnitude in a perpendicular direction.
 3. The driving mechanism of claim 2, wherein: a cut-off angle of said one of said at least two outer corners is sufficiently large to ensure there will be no mechanical interference between said final one of said spaced-apart extensions and said driver element, as said driver element moves toward its driven position.
 4. The driving mechanism of claim 1, wherein said lifter member rotates when it moves in said first direction, and its rotational motion is converted into a substantially linear motion of said driver member when said driver member moves toward its ready position.
 5. The driving mechanism of claim 1, wherein said passageway of the guide body allows said driver member to pass therethrough toward said exit end during a driving stroke and toward said receiving end during a return stroke, said driver member, when at a driven position, protruding toward said exit end of the guide body, and said driver member, when at a ready position, being withdrawn into said guide body,
 6. The driving mechanism of claim 1, wherein: (a) said lifter member, under first predetermined conditions, forces said driver member to undergo a return stroke and move toward said ready position; and (b) said driver actuation device, under second predetermined conditions, forces said driver member to undergo a driving stroke and move toward said driven position.
 7. The driving mechanism of claim 6, wherein said driver actuation device comprises a movable piston within a hollow cylinder, powered by a gas spring.
 8. A driving mechanism for use in a fastener driving tool, said driving mechanism comprising: (a) a guide body that has a receiving end, an exit end, and a passageway therebetween, said guide body being configured to receive a fastener that is to be driven from said exit end; (b) a movable driver actuation device; (c) an elongated driver member that is in mechanical communication with said movable driver actuation device at a first end of said driver member, said driver member having a second, opposite end that is sized and shaped to push a fastener from said exit end of the guide body, said driver member having a direction of movement between a driven position and a ready position, said driver member having a longitudinal edge, said driver member having a plurality of spaced-apart protrusions along said longitudinal edge; and (d) a lifter member that exhibits a contoured contact surface that, at predetermined locations along said contoured contact surface, makes contact with said plurality of spaced-apart protrusions of said driver member such that, as said lifter member is moved in a first direction, said lifter member causes said driver member to be moved from its driven position toward its ready position, said contoured contact surface comprising a plurality of spaced-apart extensions, at least one of said spaced-apart plurality of extensions having an arcuate surface for a first portion of its outer perimeter, and a cut-off face for a second portion of its outer perimeter, wherein a first outer corner provides an abrupt angular change in direction along said outer perimeter at a location between said first and second portions of said outer perimeter.
 9. The driving mechanism of claim 8, further comprising: a second outer corner that provides a second angular change in direction along a surface of said outer perimeter, such that said cut-off face is positioned between said first and second outer corners.
 10. The driving mechanism of claim 8, wherein said shape for a final one of the plurality of extensions reduces side-loading forces between said lifter member and said elongated driver member.
 11. The driving mechanism of claim 8, wherein as said lifter member rotates in said first direction to move said driver member toward said ready position, when a final one of said spaced-apart extensions reaches a position where said driver member is ready to perform a driving stroke, then one of said at least two outer corners of said final one of said spaced-apart plurality of extensions releases from contact with said driver member to allow said driver member to move toward its driven position, before a lift force side-load magnitude increases to a value equal to a lift force magnitude in a perpendicular direction.
 12. The driving mechanism of claim 11, wherein: a cut-off angle of said one of said at least two outer corners is sufficiently large to ensure there will be no mechanical interference between said final one of said spaced-apart extensions and said driver element, as said driver element moves toward its driven position.
 13. The driving mechanism of claim 8, wherein said lifter member rotates when it moves in said first direction, and its rotational motion is converted into a substantially linear motion of said driver member when said driver member moves toward its ready position.
 14. The driving mechanism of claim 8, wherein said passageway of the guide body allows said driver member to pass therethrough toward said exit end during a driving stroke and toward said receiving end during a return stroke, said driver member, when at a driven position, protruding toward said exit end of the guide body, and said driver member, when at a ready position, being withdrawn into said guide body,
 15. The driving mechanism of claim 8, wherein: (a) said lifter member, under first predetermined conditions, forces said driver member to undergo a return stroke and move toward said ready position; and (b) said driver actuation device, under second predetermined conditions, forces said driver member to undergo a driving stroke and move toward said driven position.
 16. The driving mechanism of claim 15, wherein said driver actuation device comprises a movable piston within a hollow cylinder, powered by a gas spring.
 17. A driving mechanism for use in a fastener driving tool, said driving mechanism comprising: (a) a guide body that has a receiving end, an exit end, and a passageway therebetween, said guide body being configured to receive a fastener that is to be driven from said exit end; (b) a movable driver actuation device; (c) an elongated driver member that is in mechanical communication with said movable driver actuation device at a first end of said driver member, said driver member having a second, opposite end that is sized and shaped to push a fastener from said exit end of the guide body, said driver member having a direction of movement between a driven position and a ready position, said driver member having a plurality of spaced-apart protrusions along a first longitudinal edge, said driver member having a plurality of spaced-apart openings formed in a raised wall along a second longitudinal edge that is substantially parallel to said first longitudinal edge; (d) a lifter member that exhibits a contoured contact surface that, at predetermined locations along said contoured contact surface, makes contact with said plurality of spaced-apart protrusions of said driver member such that, as said lifter member is moved in a first direction, said lifter member causes said driver member to be moved in a second direction, from its driven position toward its ready position; and (e) a movable latch member that is positioned proximal to the second longitudinal edge of said driver member, said raised wall presenting a substantially planar surface for said latch member to work against, such that said latch member may slide along said raised wall except where one of said spaced-apart opening appears in said raised wall, at which location said latch member is biased to move into said spaced-apart opening; wherein, during operation, said latch member: (i) does not prevent a movement of said driver member when the driver member moves in said second direction; (ii) under normal circumstances, does not prevent a movement of said driver member when the driver member moves in a third direction that is substantially opposite from said second direction, during a driving stroke; and (iii) under abnormal circumstances, as a safety feature, said latch member prevents a substantial movement of said driver member when the driver member moves in said third direction in the event that normal operation between said lifter member and said driver member fails.
 18. The driving mechanism of claim 17, wherein: (a) said latch member is pivotable, and is biased in a direction so as to tend to interfere with the movement of said driver member; (b) during a driving stroke under said normal circumstances, said latch member is forced to move to a non-interfering position by a latch control device; and (c) during a lifting stroke under said normal circumstances, said latch member will allow said driving member to move along a sliding surface of said latch member, and thus will not tend to prevent said lifting stroke; and (d) during said abnormal circumstances, said latch control device releases said latch member, which, being positionally biased, will tend to interfere with the movement of said driver member by moving into one of said plurality of spaced-apart openings formed in the raised wall along said second longitudinal edge of the driver member, thereby halting further movement in said driving stroke direction.
 19. The driving mechanism of claim 18, wherein said latch member is shaped without any sharp angle edges, and is sized and shaped to readily fit into one of said plurality of spaced-apart openings formed in the raised wall of the driver member.
 20. The driving mechanism of claim 18, wherein said plurality of openings formed in the raised wall are each elongated in a direction that is substantially parallel to said direction of movement of said driver member.
 21. The driving mechanism of claim 17, wherein said passageway of the guide body allows said driver member to pass therethrough toward said exit end during a driving stroke and toward said receiving end during a return stroke, said driver member, when at a driven position, protruding toward said exit end of the guide body, and said driver member, when at a ready position, being withdrawn into said guide body,
 22. The driving mechanism of claim 17, wherein: (a) said lifter member, under first predetermined conditions, forces said driver member to undergo a return stroke and move toward said ready position; and (b) said driver actuation device, under second predetermined conditions, forces said driver member to undergo a driving stroke and move toward said driven position.
 23. The driving mechanism of claim 22, wherein said driver actuation device comprises a movable piston within a hollow cylinder, powered by a gas spring. 